Roll press device and control device

ABSTRACT

A thickness meter detects a thickness of an electrode plate of a secondary battery at three or more points in a width direction of the electrode plate. A calculator calculates three feature amounts of a first deviation between the thickness target value and a thickness measurement value of a point closest to a first compression mechanism among the three or more points, a second deviation between the thickness target value and a thickness measurement value of a point closest to a second compression mechanism among the three or more points, and a secondary component of a thickness profile of the electrode plate from thickness measurement values at the three or more points and the thickness target value, and adaptively changes the setting values of the first compression mechanism, the second compression mechanism, a first bend mechanism, and a second bend mechanism on the basis of the three feature amounts.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is the U.S. National Phase under 35 U.S.C. § 371 ofInternational Patent Application No. PCT/JP2020/042738, filed on Nov.17, 2020, which in turn claims the benefit of Japanese PatentApplication No. 2020-002269, filed on Jan. 9, 2020, the entire contentof each of which is incorporated herein by reference.

TECHNICAL FIELD

The present disclosure relates to a roll press device that rolls anelectrode plate of a secondary battery, and a control device.

BACKGROUND ART

In recent years, with the spread of electric vehicles (EV), hybridvehicles (HV), and plug-in hybrid vehicles (PHV), shipment of secondarybatteries increases. In particular, shipment of lithium ion secondarybatteries increases. A general secondary battery includes a positiveelectrode, a negative electrode, a separator, and an electrolyticsolution as main components. In a compression processing step which isone of steps of manufacturing a positive electrode plate and a negativeelectrode plate of the secondary battery, a roll press device is used(for example, refer to Patent Literature 1).

CITATION LIST Patent Literature [Patent Literature 1] JP 2013-111647 ASUMMARY OF INVENTION

In a compression processing step of an electrode plate in the roll pressdevice, generally, thickness accuracy of about 2 μm or less is required.A change in the coating film thickness of an electrode material in aprevious step or a change in the roll outer diameter due to processingheat or bearing heat caused by compression in a compression step causesa change in the thickness in a length direction or a width direction ofthe electrode plate during the compression processing. When thethickness exceeds a range to be controlled, it is necessary to stop theline and manually reset the press conditions to adjust the thicknesswithin the control range, and it is necessary to remove the thicknessportion that cannot be applied to the product, so that a decrease infacility operation rate and a decrease in yield occur.

In recent years, secondary batteries have been increasingly required tobe small, lightweight, and have a high capacity, or have a high capacityat the same manufacturing cost. In the battery design, the length of theelectrode is determined such that both a cylindrical shape and arectangular shape are accommodated in a battery case. Even with the sameelectrode length, the winding diameter when the electrode is woundincreases as the thickness increases. Therefore, the length of theelectrode is determined in consideration of a range of thicknessvariations that occur in manufacturing. That is, if thickness accuracycan be increased, the length of the electrode can be increased, so thata battery having a higher capacity can be designed.

In order to solve the above problems, a roll press device according toan aspect of the present disclosure includes: a first pressure rollerand a second pressure roller structured to roll an electrode plate of asecondary battery to be continuously conveyed by sandwiching theelectrode plate; a first main bearing and a second main bearing providedon one side and the other side of a rotation shaft of the first pressureroller, respectively, and structured to rotatably support the rotationshaft; a third main bearing and a fourth main bearing provided on oneside and the other side of a rotation shaft of the second pressureroller, respectively, and structured to rotatably support the rotationshaft; a first bend bearing and a second bend bearing provided on oneside and the other side of the rotation shaft of the first pressureroller, respectively, and structured to rotatably support the rotationshaft; a third bend bearing and a fourth bend bearing provided on oneside and the other side of the rotation shaft of the second pressureroller, respectively, and structured to rotatably support the rotationshaft; a first compression mechanism capable of applying a load to atleast one of the first main bearing and the third main bearing in adirection in which the first pressure roller and the second pressureroller approach each other; a second compression mechanism capable ofapplying a load to at least one of the second main bearing and thefourth main bearing in a direction in which the first pressure rollerand the second pressure roller approach each other; a first bendmechanism capable of applying a load to at least one of the first bendbearing and the third bend bearing in a direction in which the firstpressure roller and the second pressure roller are separated from eachother; a second bend mechanism capable of applying a load to at leastone of the second bend bearing and the fourth bend bearing in adirection in which the first pressure roller and the second pressureroller are separated from each other; a thickness meter provided on theexit side of the first pressure roller and the second pressure rollerand structured to detect a thickness of the electrode plate of thesecondary battery at three or more points in a width direction of theelectrode plate; a calculator structured to calculate setting values ofthe first compression mechanism, the second compression mechanism, thefirst bend mechanism, and the second bend mechanism on the basis ofthickness measurement values at the three or more points based ondetection values of the thickness meter and a thickness target value;and a controller structured to control loads of the first compressionmechanism, the second compression mechanism, the first bend mechanism,and the second bend mechanism on the basis of the setting valuescalculated by the calculator. The calculator calculates three featureamounts of a first deviation between the thickness target value and athickness measurement value of a point closest to the first compressionmechanism among the three or more points, a second deviation between thethickness target value and a thickness measurement value of a pointclosest to the second compression mechanism among the three or morepoints, and a secondary component of a thickness profile of theelectrode plate, and adaptively changes the setting values of the firstcompression mechanism, the second compression mechanism, the first bendmechanism, and the second bend mechanism on the basis of the threefeature amounts.

According to the present disclosure, it is possible to realize highaccuracy of thickness control of a roll press device.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic front view of a roll press device according to afirst embodiment.

FIG. 2 is a schematic front view of a roll press device according to asecond embodiment.

FIG. 3 is a schematic front view of a roll press device according to athird embodiment.

FIG. 4 is a schematic side view of the roll press devices according tothe first to third embodiments.

FIG. 5 is a diagram illustrating a feedback control example 1 using afirst control panel and a second control panel.

FIG. 6 is a diagram illustrating a feedback control example 2 using thefirst control panel and the second control panel.

FIG. 7 is a diagram illustrating a feedback control example 3 using thefirst control panel and the second control panel.

FIG. 8 is a diagram illustrating a feedback control example 4 using thefirst control panel and the second control panel.

FIG. 9 is a diagram plotting a relation between a change in line speedand a change in thickness of an electrode plate under a constantpress-bend condition in a certain roll press device.

FIG. 10 is a diagram illustrating a feedforward control example 1 usingthe first control panel.

FIG. 11 is a diagram illustrating a feedforward control example 2 usingthe first control panel.

FIG. 12 is a diagram illustrating a feedforward control example 3 usingthe first control panel.

DESCRIPTION OF EMBODIMENTS

FIG. 1 is a schematic front view of a roll press device according to afirst embodiment. A first pressure roller 11 and a second pressureroller 12 are a pair of upper and lower roll bites, and are installed toface each other in a contactable and separable manner. The pair of firstpressure roller 11 and second pressure roller 12 rolls an electrodeplate 2 by sandwiching the electrode plate 2 of a secondary battery tobe continuously conveyed. The electrode plate 2 of the secondary batterypassed through the roll press device is a sheet-shaped electrodematerial obtained by applying a slurry containing an active material toa metal foil and drying it. For example, a positive electrode plate of alithium ion secondary battery is produced by applying a slurrycontaining a positive electrode active material such as lithium cobaltoxide or lithium iron phosphate on an aluminum foil. In addition, anegative electrode plate of the lithium ion secondary battery isproduced by applying a slurry containing a negative electrode activematerial such as graphite on a copper foil. The thickness of the appliedactive material accounts for most of the thickness of the electrodeplate 2 passed through the roll press device.

A first main bearing 21 and a second main bearing 22 are provided on oneside and the other side of a rotation shaft of the first pressure roller11, respectively, and rotatably support the rotation shaft. A third mainbearing 23 and a fourth main bearing 24 are provided on one side and theother side of a rotation shaft of the second pressure roller 12,respectively, and rotatably support the rotation shaft.

A first bend bearing 31 and a second bend bearing 32 are provided on oneside and the other side of the rotation shaft of the first pressureroller 11, respectively, and rotatably support the rotation shaft. Athird bend bearing 33 and a fourth bend bearing 34 are provided on oneside and the other side of the rotation shaft of the second pressureroller 12, respectively, and rotatably support the rotation shaft.

In the example illustrated in FIG. 1 , each of the first main bearing 21to the fourth main bearing 24 and the first bend bearing 31 to thefourth bend bearing 34 is formed of a bearing box incorporating abearing that rotatably supports the rotation shaft of the roller.

A first compression mechanism 41 is a mechanism capable of compressingthe electrode plate 2 by applying a load to at least one of the firstmain bearing 21 or the third main bearing 23 in a direction in which thefirst pressure roller 11 and the second pressure roller 12 approach eachother. A second compression mechanism 42 is a mechanism capable ofcompressing the electrode plate 2 by applying a load to at least one ofthe second main bearing 22 or the fourth main bearing 24 in a directionin which the first pressure roller 11 and the second pressure roller 12approach each other.

In the first embodiment, as the first compression mechanism 41, a firstpress cylinder 41 a capable of applying a load to the third main bearing23 and a first electric screw 41 b capable of applying a load to thefirst main bearing 21 are provided. As the second compression mechanism42, a second press cylinder 42 a capable of applying a load to thefourth main bearing 24 and a second electric screw 42 b capable ofapplying a load to the second main bearing 22 are provided. For pressurecontrol of the first press cylinder 41 a and the second press cylinder42 a, for example, a hydraulic servo valve or a pressure reducing valvecan be used. A servomotor is used for position control of the firstelectric screw 41 b and the second electric screw 42 b. A pressurereduction amount of each of the first electric screw 41 b and the secondelectric screw 42 b is controlled by each servomotor, and the loadsapplied to the first main bearing 21 and the second main bearing 22 bythe first electric screw 41 b and the second electric screw 42 b arecontrolled.

A first bend mechanism 51 (in the first embodiment, a first bendcylinder 51 a) is a mechanism that is provided between the first bendbearing 31 and the third bend bearing 33, and can correct the deflectionof the roller by applying a load in a direction in which the firstpressure roller 11 and the second pressure roller 12 are separated fromeach other. A second bend mechanism 52 (in the first embodiment, asecond bend cylinder 52 a) is a mechanism that is provided between thesecond bend bearing 32 and the fourth bend bearing 34, and can correctthe deflection of the roller by applying a load in a direction in whichthe first pressure roller 11 and the second pressure roller 12 areseparated from each other.

A roll gap between the first pressure roller 11 and the second pressureroller 12 is controlled by changing the pressure of the firstcompression mechanism 41 and/or the second compression mechanism 42 by apress pressure controller 817 a (refer to FIG. 5 ) to be describedlater. The roll deflection also changes with the change of the roll gap.A roll deflection amount can be corrected by changing the pressure ofthe first bend mechanism 51 and/or the second bend mechanism 52 by abend pressure controller 818 a (refer to FIG. 5 ) to be described later.At that time, the roll gap also changes and acts in a reverse manner tothe pressure change by the first compression mechanism 41 and/or thesecond compression mechanism 42.

A first preload mechanism 61 (in the example illustrated in FIG. 1 , afirst preload cylinder 61 a) is a mechanism that applies a constant loadto the first bend bearing 31 in a direction in which the first pressureroller 11 and the second pressure roller 12 are separated from eachother. A second preload mechanism 62 (in the example illustrated in FIG.1 , a second preload cylinder 62 a) is a mechanism that applies aconstant load to the second bend bearing 32 in a direction in which thefirst pressure roller 11 and the second pressure roller 12 are separatedfrom each other. The pressures of the first preload cylinder 61 a andthe second preload cylinder 62 a are fixed and are always set to thesame pressure.

In the example illustrated in FIG. 1 , the first preload mechanism 61and the second preload mechanism 62 apply a preload load equal to ormore than the weight of the first pressure roller 11 to the first bendbearing 31 and the second bend bearing 32. As a result, the firstpressure roller 11 is moderately pressed (pulled) upward to reduce aninfluence of rattling of the roll press device. Note that the firstpreload mechanism 61 and the second preload mechanism 62 can be omitted.

FIG. 2 is a schematic front view of a roll press device according to asecond embodiment. Hereinafter, differences from the configuration ofthe first embodiment will be described. In the first embodiment, thefirst bend mechanism 51 and the second bend mechanism 52 of a type inwhich the first bend cylinder 51 a and the second bend cylinder 52 a areprovided between the first bend bearing 31 and the second bend bearing32 on the upper side and the third bend bearing 33 and the fourth bendbearing 34 on the lower side, and a load is applied in a direction inwhich the first pressure roller 11 and the second pressure roller 12 areseparated from each other are adopted.

In the second embodiment, as the first bend mechanism 51 and the secondbend mechanism 52, a third bend cylinder 51 b is provided outside thefirst bend bearing 31, a fourth bend cylinder 52 b is provided outsidethe second bend bearing 32, a fifth bend cylinder 51 c is providedoutside the third bend bearing 33, and a sixth bend cylinder 52 c isprovided outside the fourth bend bearing 34. In the second embodiment, atype in which a load is applied in a direction in which the firstpressure roller 11 and the second pressure roller 12 are separated fromeach other by the third bend cylinder 51 b, the fourth bend cylinder 52b, the fifth bend cylinder 51 c, and the sixth bend cylinder 52 c isadopted. In the second embodiment, the first preload mechanism 61 andthe second preload mechanism 62 are not provided.

In the second embodiment, the first compression mechanism 41 includes afirst press cylinder 41 a, a first magnescale 41 c, and a first loadcell 41 d. In the second embodiment, a hydraulic servo valve is used forpressure control of the first press cylinder 41 a. The first magnescale41 c detects a position of the first press cylinder 41 a. In the secondembodiment, a load due to the weight of the first pressure roller 11 isapplied to the first main bearing 21. The first load cell 41 d is acompression type load cell, and detects a load applied to the first mainbearing 21. Since a configuration of the second compression mechanism 42is the same as that of the first compression mechanism 41, thedescription thereof will be omitted. In the second embodiment, the firstelectric screw 41 b and the second electric screw 42 b are not provided.

FIG. 3 is a schematic front view of a roll press device according to athird embodiment. Hereinafter, differences from the configuration of thefirst embodiment will be described. A first bend mechanism 51 and asecond bend mechanism 52 according to the third embodiment adopt thesame types as those of the first bend mechanism 51 and the second bendmechanism 52 according to the second embodiment.

The first compression mechanism 41 and the second compression mechanism42 according to the third embodiment are provided with a first electriccotter 41 e and a second electric cotter 42 e instead of the firstelectric screw 41 b and the second electric screw 42 b according to thefirst embodiment. The first load cell 41 d and the second load cell 42 dare not provided. In general, the roll press device according to thethird embodiment can be manufactured at a lower cost than the roll pressdevices according to the first and second embodiments.

The first electric cotter 41 e is provided between the first mainbearing 21 and the third main bearing 23. The first electric cotter 41 eincludes an upper cotter fixed to the first main bearing 21 and a lowercotter fixed to the third main bearing 23. A bottom surface of the uppercotter and a top surface of the lower cotter are tapered surfaces, andthe tapered surfaces are disposed to face each other. The lower cotteris provided with a linear servo motor for sliding the lower cotter in aleft-right direction (a direction of the tapered surface). The lowercotter is slid in the left-right direction, so that a height of thefirst electric cotter 41 e can be adjusted. In the example illustratedin FIG. 3 , when the lower cotter slides leftward, the height of thefirst electric cotter 41 e decreases, and when the lower cotter slidesrightward, the height of the first electric cotter 41 e increases. Thatis, as the lower cotter slides leftward, a load in a direction in whichthe first pressure roller 11 and the second pressure roller 12 approacheach other increases.

The second electric cotter 42 e is provided between the second mainbearing 22 and the fourth main bearing 24. The second electric cotter 42e includes an upper cotter fixed to the second main bearing 22 and alower cotter fixed to the fourth main bearing 24. Since a configurationof the second electric cotter 42 e is the same as that of the firstelectric cotter 41 e, the description thereof will be omitted.

FIG. 4 is a schematic side view of the roll press device 1 according toeach of the first to third embodiments. An unwinder 13 is installed onthe entry side of the pair of first pressure roller 11 and secondpressure roller 12, and a winder 14 is installed on the exit side. Theunwinder 13 unwinds the sheet-like electrode plate 2 wound in a coilshape toward the pair of first pressure roller 11 and second pressureroller 12. The winder 14 winds the electrode plate 2 compressed by thepair of first pressure roller 11 and second pressure roller 12 into acoil shape.

A motor 15 is a motor that drives the first pressure roller 11 and thesecond pressure roller 12. A pulse generator 16 is attached to thedriving motor 15 and detects a rotation speed of the motor 15.

A thickness meter 70 is provided on the exit side of the pair of firstpressure roller 11 and second pressure roller 12, and detects thethickness of the electrode plate 2 at each of three points of a firstpoint, a second point, and a third point arranged in a width directionof the electrode plate 2. The first point is set at an end portion ofthe electrode plate 2 on the side where the first compression mechanism41 is provided. The second point is set at a center portion of theelectrode plate 2. The third point is set at an end portion of theelectrode plate 2 on the side where the second compression mechanism 42is provided.

In the general roll press device 1, a screen operated by an operator isinstalled on the side (the side of the second compression mechanism 42in the first to third embodiments) opposite to the side (the side of thefirst compression mechanism 41 in the first to third embodiments) wherethe motor 15 is installed. Therefore, hereinafter, in the first to thirdembodiments, the first point is referred to as the driving side, thesecond point is referred to as the center portion, and the third pointis referred to as the operation side. That is, the thickness meter 70detects the thickness of each of the driving side, the center portion,and the operation side of the electrode plate 2 after the compressionprocessing.

The thickness meter 70 may extract the thickness of each of the drivingside, the center portion, and the operation side by continuouslydetecting the thickness of the electrode plate 2 by scanning onethickness detection sensor in the width direction of the electrode plate2.

In the thickness meter 70, three thickness detection sensors may befixed and installed on the driving side, the center portion, and theoperation side, respectively, and the thicknesses of the driving side,the center portion, and the operation side may be detected by the threethickness detection sensors, respectively.

As a detection method of the thickness meter 70, a method for detectingdistances to both surfaces of the electrode plate 2 using a laser sensoror an optical sensor and detecting a thickness from a positionalrelation thereof may be used. In addition, a method may be used in whicha change in eddy current is detected by a magnetic sensor to detect adistance to an outer diameter surface of the electrode plate 2, adistance to a surface of the electrode plate 2 on a guide roll isdetected by a laser sensor or an optical sensor, and a thickness isdetected from a positional relation between the guide roll and thesurface of the electrode plate 2. Note that the distance to the surfaceof the electrode plate 2 may be detected using a white confocal sensor.

A control device 80 is a device for controlling the entire roll pressdevice 1, and includes a first control panel 81 and a second controlpanel 82 in the example illustrated in FIG. 4 . The first control panel81 is a control panel of a press system, and the second control panel 82is a control panel of a thickness system. A rotation pulse generated bythe pulse generator 16 is input to the first control panel 81. Athickness detection value detected by the thickness meter 70 is input tothe second control panel 82. The configuration described using FIG. 4 iscommon to the first to third embodiments.

FIG. 5 is a diagram illustrating a feedback control example 1 using thefirst control panel 81 and the second control panel 82. The feedbackcontrol example 1 is control used in the roll press device according tothe first embodiment illustrated in FIG. 1 . In the feedback controlexample 1, the first press cylinder 41 a and the second press cylinder42 a are used as the compression mechanism. The first bend cylinder 51 aand the second bend cylinder 52 a are used as the bend mechanism. Thefirst control panel 81 includes a programmable logic controller (PLC), apersonal computer (PC), a human machine interface (HMI), an actuatorcontroller, and the like. The second control panel includes a PLC, a PC,a sensor controller, and the like.

A program operating in the PLC is generated by a dedicated applicationin the PC and downloaded to the PLC. The PLC receives productinformation of the electrode plate 2 from a manufacturing executionsystem (MES). Various setting values input to the operator via the HMIare input to the PLC. In the feedback control example 1, the settingvalues include a thickness target value of the electrode plate 2,pressure setting values of the first press cylinder 41 a and the secondpress cylinder 42 a, and pressure setting values of the first bendcylinder 51 a and the second bend cylinder 52 a. The HMI receives aninput from the operator, displays a driving situation, an alarm, and thelike, and outputs a sound.

FIG. 5 illustrates functional blocks realized by the first control panel81 and the second control panel 82 related to the feedback controlexample 1. The first control panel 81 includes a length measurer 811, anacquisition timing generator 812, a thickness measurement value acquirer813, a feature amount calculator 814, a correction value calculator 815,a setting value corrector 816, a press pressure controller 817 a, a PIDcontroller 817 b, a press pressure deviation calculator 817 c, a bendpressure controller 818 a, a PID controller 818 b, and a bend pressuredeviation calculator 818 c. The second control panel 82 includes athickness measurement value calculator 821.

A rotation pulse is input from the pulse generator 16 to the lengthmeasurer 811. The length measurer 811 estimates the rotation speeds ofthe first pressure roller 11 and the second pressure roller 12 on thebasis of the input rotation pulse, and estimates the speed of theelectrode plate 2 passing between the first pressure roller 11 and thesecond pressure roller 12. The length measurer 811 measures a length(distance) of the electrode plate 2 traveling per unit time, on thebasis of the estimated speed of the electrode plate 2. The lengthmeasurer 811 supplies the measured length of the electrode plate 2 tothe acquisition timing generator 812 and the thickness measurement valuecalculator 821.

The thickness measurement value calculator 821 receives the respectivethickness detection values of the driving side, the center portion, andthe operation side from the thickness meter 70. In addition, the lengthof the electrode plate 2 is input from the length measurer 811.

When three thickness detection sensors are fixed and the thickness isdetected in the thickness meter 70, the thickness measurement valuecalculator 821 averages each of the three thickness detection values inthe length direction (traveling direction) of the electrode plate 2 andperforms filtering in order to remove a high-cycle thickness variationthat does not need to be controlled. It is desirable to calculate anaverage value of 5 mm or more in the traveling direction in order toremove a steep change in the traveling direction due to application pumppulsation or the like in an application step.

For example, in a case where the thickness detection value is inputevery 1 mm pitch, the thickness measurement value calculator 821calculates a moving average value of five points in the travelingdirection and uses the calculated value as the measurement value. Inaddition, an average value of three points excluding the two mostdeviating points among the five points detected in the travelingdirection may be calculated and used as the measurement value. When themoving average value is calculated, the thickness measurement valuecalculator 821 uses the length of the electrode plate 2 input from thelength measurer 811 as a synchronization signal. Note that a detectionvalue corresponding to a non-coated portion corresponding to a slit inthe width direction of the electrode plate 2 or a portion coated only onone side is removed.

In the case where the thickness meter 70 scans one thickness detectionsensor in the width direction of the electrode plate 2 to detect thethickness, the thickness measurement value calculator 821 may calculatean average value of detection values in a width range of each of thedriving side, the center portion, and the operation side set in advanceand use the average value as the measurement value. Furthermore, themeasurement values may be averaged in the traveling direction asdescribed above to obtain a final measurement value.

The thickness measurement value calculator 821 supplies the calculateddriving-side thickness measurement value T_(m), center thicknessmeasurement value T_(c), and operation-side thickness measurement valueT_(s) to the thickness measurement value acquirer 813.

The acquisition timing generator 812 generates timing at which thethickness measurement value acquirer 813 acquires the driving-sidethickness measurement value T_(m), the center thickness measurementvalue T_(c), and the operation-side thickness measurement value T_(s)supplied from the thickness measurement value calculator 821, andsupplies the generated timing to the thickness measurement valueacquirer 813.

There is a distance L_(t) (pass line length L_(t)) between a pressposition by the first pressure roller 11 and the second pressure roller12 and the thickness meter 70. Therefore, a time lag occurs until thethickness meter 70 detects the thickness change caused by the pressurechange by the first pressure roller 11 and the second pressure roller12. Further, a time lag t_(d) also occurs until the actual pressurechange of the compression mechanism and/or the bend mechanism iscompleted after the pressure setting value of the compression mechanismand/or the bend mechanism is changed.

Among the press cylinder controlled by the hydraulic servo valve, thepress cylinder controlled by the pressure reducing valve, the electricscrew, and the electric cotter, the press cylinder controlled by thehydraulic servo valve has the highest responsiveness, and the controlsystem time lag t_(d) is the smallest when the press cylinder controlledby the hydraulic servo valve is used.

The pass line length L_(t) and the control system time lag t_(d) areactually measured in advance, and the actually measured values are setas fixed values in the acquisition timing generator 812. The acquisitiontiming generator 812 uses a length parameter L to be compared with thepass line length L_(t) and a time parameter t to be compared with thecontrol system time lag t_(d). The acquisition timing generator 812increments the length parameter L on the basis of the length of theelectrode plate 2 supplied from the length measurer 811, and incrementsthe control system time lag t_(d) on the basis of a clock supplied froma clock.

When the pressure setting value of at least one of the first presscylinder 41 a, the second press cylinder 42 a, the first bend cylinder51 a, or the second bend cylinder 52 a is changed by the setting valuecorrector 816, the acquisition timing generator 812 resets the lengthparameter L and the time parameter t to zero. When the length parameterL exceeds the pass line length L_(t) and the time parameter t exceedsthe control system time lag t_(d), the acquisition timing generator 812supplies the acquisition timing to the thickness measurement valueacquirer 813.

A state in which the length parameter L exceeds the pass line lengthL_(t) and the time parameter t exceeds the control system time lag t_(d)is a state in which a change in the thickness of the electrode plate 2due to a change in the pressure setting value of at least one of thefirst press cylinder 41 a, the second press cylinder 42 a, the firstbend cylinder 51 a, or the second bend cylinder 52 a is reflected in thedetection value of the thickness meter 70.

On the other hand, a state in which the length parameter L does notexceed the pass line length L_(t) or a state in which the time parametert does not exceed the control system time lag t_(d) is a state in whicha change in the thickness of the electrode plate 2 due to a change inthe pressure setting value of at least one of the first press cylinder41 a, the second press cylinder 42 a, the first bend cylinder 51 a, orthe second bend cylinder 52 a is not yet reflected in the detectionvalue of the thickness meter 70. This state is a state in which aninfluence of the change in the pressure setting value on the thicknessof the electrode plate 2 has not been able to be confirmed.

Therefore, it is necessary to wait until the length parameter L exceedsthe pass line length L_(t) and the time parameter t exceeds the controlsystem time lag t_(d), and a next change of a pressure setting value issuspended until this state is reached. As a result, useless or excessivechanges of the pressure setting values of the first press cylinder 41 a,the second press cylinder 42 a, the first bend cylinder 51 a, and thesecond bend cylinder 52 a are avoided, and the pressure setting valuescan be efficiently adjusted.

The thickness measurement value acquirer 813 acquires the driving-sidethickness measurement value T_(m), the center thickness measurementvalue T_(c), and the operation-side thickness measurement value T_(s)supplied from the thickness measurement value calculator 821 at thetiming supplied from the acquisition timing generator 812, and suppliesthem to the feature amount calculator 814.

The driving-side thickness measurement value T_(m), the center thicknessmeasurement value T_(c), and the operation-side thickness measurementvalue T_(s) are input from the thickness measurement value acquirer 813to the feature amount calculator 814. Further, a thickness target valueT_(t) set by the operator is input to the feature amount calculator 814.

On the basis of the driving-side thickness measurement value T_(m), thecenter thickness measurement value T_(c), the operation-side thicknessmeasurement value T_(s), and the thickness target value T_(t), thefeature amount calculator 814 calculates three deviation feature amountsdefined by the following (Formula 1) to (Formula 3) as a thicknessfeature amount to be controlled. A first feature amount T_(t−m) isdefined by a difference between the thickness target value T_(t) and thedriving-side thickness measurement value T_(m). A second feature amountT_(t−s) is defined by a difference between the thickness target valueT_(t) and the operation-side thickness measurement value T_(s). A thirdfeature amount T_(drop) is defined by a difference between the centerthickness measurement value T_(c) and an average value of thedriving-side thickness measurement value T_(m) and the operation-sidethickness measurement value T_(s).

T _(t−m) =T _(t) −T _(m)  (Formula 1)

T _(t−s) =T _(t) −T _(s)  (Formula 2)

T _(drop) =T _(c) −T _(ms,ave) =T _(c)−(T _(m) +T _(s))/2  (Formula 3)

When the first feature amount T_(t−m)=0, the second feature amountT_(t−s)=0, and the third feature amount T_(drop)=0 are set, thedriving-side thickness measurement value T_(m)=the center thicknessmeasurement value T_(e)=the operation-side thickness measurement valueT_(s)=the thickness target value T_(t) is obtained. The third featureamount T_(drop) represents a secondary component (parabolic shape convexupward when a numerical value is large) of a thickness profile, andchanges depending on the magnitude of the roll deflection and thedirection of the roll deflection.

The feature amount calculator 814 supplies the calculated first featureamount T_(t−m), second feature amount T_(t−s), and third feature amountT_(drop) to the correction value calculator 815.

According to experiments by the present inventors, it has been foundthat there are relations defined by the following (Formula 4) to(Formula 6) between the first feature amount T_(t−m), the second featureamount T_(t−s), and the third feature amount T_(drop) and the load.

T _(t−m)∝(driving-side load)  (Formula 4)

T _(t−s)∝(operation-side load)  (Formula 5)

T _(drop) ∝A×(total press load)−B×(total bend load)−C×(total preloadload)  (Formula 6)

Here, the total press load is the sum of the driving-side press load andthe operation-side press load, the total bend load is the sum of thedriving-side bend load and the operation-side bend load, and the totalpreload load is the sum of the driving-side preload load and theoperation-side preload load. The driving-side load is a driving-sideload generated by the driving-side press cylinder, the driving-side bendcylinder, and the driving-side preload cylinder. The operation-side loadis an operation-side load generated by the operation-side presscylinder, the operation-side bend cylinder, and the operation-sidepreload cylinder.

The press cylinder load acts in a direction of applying a pressure to amaterial to be rolled, and the bend load and the preload load act in adirection of reducing the pressure to the material to be rolled. Thepreload cylinder load is set to a fixed value at which a pressure thatdoes not excessively generate the roll deflection and a press pressurethat can reduce the rattling and vibration of a facility are secured.That is, the preload load is not changed in the thickness control. Whenthe preload cylinder load is excessively large, it is difficult tocontrol the roll deflection within a control range of the press pressureand the bend pressure. In a case of a facility in which the firstpreload cylinder 61 a and the second preload cylinder 62 a are notprovided, the preload load is zero.

A, B, and C in the above (Formula 6) are positive constants, andindicate that an influence of the difference between the driving-sideload and the operation-side load of each of the total press load, thetotal bend load, and the total preload load on the third feature amountT_(drop) is different.

By measuring proportional constants of a left side and a right side ofeach of the above (Formula 4) to (Formula 6) in advance, when the totalpreload load is a constant value or when the preload mechanism is notprovided, the total press load and the total bend load that cause thefirst feature amount T_(t−m), the second feature amount T_(t−s), and thethird feature amount T_(drop) to be zero at the same time can beuniquely obtained from the above (Formula 4) to (Formula 6).

In the feedback control example 1, each load is controlled bycontrolling the pressure of each cylinder. The load is calculated bycylinder diameter (constant)×cylinder pressure. From the above (Formula4) to (Formula 6), relations of the following (Formula 7) to (Formula15) hold between a driving-side press pressure P_(m), an operation-sidepress pressure P_(s), a driving-side bend pressure B_(m), anoperation-side bend pressure B_(s), a driving-side preload pressureR_(m), an operation-side preload pressure R_(s), an average presspressure P_(ave)=(P_(m)+P₃)/2, an average bend pressureB_(ave)=(B_(m)+B_(s))/2, and an average preload pressureR_(ave)=(R_(m)+R_(s))/2 and the first feature amount T_(t−m), the secondfeature amount T_(t−s), and the third feature amount T_(drop).Specifically, the following (Formula 7) to (Formula 9) are derived fromthe above (Formula 4), the following (Formula 10) to (Formula 12) arederived from the above (Formula 5), and the following (Formula 13) to(Formula 15) are derived from the above (Formula 6).

T _(t−n) ∝P _(m)  (Formula 7)

T _(t−n) ∝−B _(m)  (Formula 8)

T _(t−n) ∝−R _(m)  (Formula 9)

T _(t−s) ∝P _(s)  (Formula 10)

T _(t−s) ∝−B _(s)  (Formula 11)

T _(t−s) ∝−R _(s)  (Formula 12)

T _(drop) ∝P _(ave)  (Formula 13)

T _(drop) ∝−B _(ave)  (Formula 14)

T _(drop) ∝−R _(ave)  (Formula 15)

The proportional constants of the above (Formula 7) and (Formula 8), theabove (Formula 10) and (Formula 11), and the above (Formula 13) and(Formula 14) are measured in advance. In a case where a pressuredifference between the driving-side bend pressure B_(m) and theoperation-side bend pressure B_(s) is caused to be constant when thepreload pressure is constant or when the preload mechanism is notprovided, a driving-side press pressure correction value ΔP_(m) and anoperation-side press pressure correction value ΔP_(s) of thedriving-side press pressure P_(m) and the operation-side press pressureP_(s) at which the first feature amount T_(t−m) and the second featureamount T_(t−s) become zero at the same time are obtained from thecorrelations shown in the above (Formula 7) and (Formula 10).

From the correlation shown in the above (Formula 13), a change amount ofthe third feature amount T_(drop) associated with the correction of thedriving-side press pressure P_(m) and the operation-side press pressureP_(s) described above is obtained. A correction value ΔB_(ave) of theaverage bend pressure B_(ave) for causing the third feature amountT_(drop) to be zero is obtained on the basis of the correlation shown inthe above (Formula 14) and the change amount of the third feature amountT_(drop). Since the difference between the driving-side bend pressureB_(m) and the operation-side bend pressure B_(s) is constant, thedriving-side bend pressure correction value ΔB_(m) and theoperation-side bend pressure correction value ΔB_(s) of the driving-sidebend pressure B_(m) and the operation-side bend pressure B_(s) areobtained.

The thickness over the entire width of the electrode plate 2 can becontrolled to the target value T_(t) by controlling the pressure of eachcylinder such that the pressure of the first press cylinder 41 a becomesa corrected driving-side press pressure setting value P_(m)+ΔP_(m), thepressure of the second press cylinder 42 a becomes a correctedoperation-side press pressure setting value P_(s)+ΔP_(s), the pressureof the first bend cylinder 51 a becomes a corrected driving-side bendpressure setting value B_(m)+ΔB_(m), and the pressure of the second bendcylinder 52 a becomes a corrected operation-side bend pressure settingvalue B_(s)+ΔB_(s).

The correction value calculator 815 is supplied with the first featureamount T_(t−m), the second feature amount T_(t−s), and the third featureamount T_(drop) from the feature amount calculator 814. In addition, thedriving-side press pressure setting value P_(m), the operation-sidepress pressure setting value P_(s), the driving-side bend pressuresetting value B_(m), and the operation-side bend pressure setting valueB_(s) input by the operator via the HMI are supplied. The values derivedin advance are set to the driving-side press pressure setting valueP_(m), the operation-side press pressure setting value P_(s), thedriving-side bend pressure setting value B_(m), and the operation-sidebend pressure setting value B_(s) such that all of the first featureamount T_(t−m), the second feature amount T_(t−s), and the third featureamount T_(drop) become zero under the standard condition.

The correction value calculator 815 calculates the driving-side presspressure correction value ΔP_(m), the operation-side press pressurecorrection value ΔP_(s), the driving-side bend pressure correction valueΔB_(m), and the operation-side bend pressure correction value ΔB_(s), onthe basis of the first feature amount T_(t−m), the second feature amountT_(t−s), the third feature amount T_(drop), and the proportionalconstants of the above (Formula 7), (Formula 8), (Formula 10), (Formula11), (Formula 13), and (Formula 14). The correction value calculator 815supplies the calculated driving-side press pressure correction valueΔP_(m), operation-side press pressure correction value ΔP_(s),driving-side bend pressure correction value ΔB_(m), and operation-sidebend pressure correction value ΔB_(s) to the setting value corrector816.

The setting value corrector 816 is supplied with the driving-side presspressure correction value ΔP_(m), the operation-side press pressurecorrection value ΔP_(s), the driving-side bend pressure correction valueΔB_(m), and the operation-side bend pressure correction value ΔB_(s)from the correction value calculator 815. In addition, the driving-sidepress pressure setting value P_(m), the operation-side press pressuresetting value P_(s), the driving-side bend pressure setting value B_(m),and the operation-side bend pressure setting value B_(s) input by theoperator via the HMI are supplied.

The setting value corrector 816 adds the driving-side press pressurecorrection value ΔP_(m), the operation-side press pressure correctionvalue ΔP_(s), the driving-side bend pressure correction value ΔB_(m),and the operation-side bend pressure correction value ΔB_(s) to thedriving-side press pressure setting value P_(m), the operation-sidepress pressure setting value P_(s), the driving-side bend pressuresetting value B_(m), and the operation-side bend pressure setting valueB_(s), respectively, and calculates the corrected driving-side presspressure setting value P_(m)+ΔP_(m), the corrected operation-side presspressure setting value P_(s)+ΔP_(s), the corrected driving-side bendpressure setting value B_(m)+ΔB_(m), and the corrected operation-sidebend pressure setting value B_(s)+ΔB_(s).

The setting value corrector 816 supplies the calculated correcteddriving-side press pressure setting value P_(m)+ΔP_(m) and correctedoperation-side press pressure setting value P_(s)+ΔP_(s) to the presspressure deviation calculator 817 c, and supplies the correcteddriving-side bend pressure setting value B_(m)+ΔB_(m) and the correctedoperation-side bend pressure setting value B_(s)+ΔB_(s) to the bendpressure deviation calculator 818 c.

The press pressure deviation calculator 817 c calculates a deviationbetween the corrected driving-side press pressure setting valueP_(m)+ΔP_(m) supplied from the setting value corrector 816 and theactually measured pressure value of the first press cylinder 41 a and adeviation between the corrected operation-side press pressure settingvalue P_(s)+ΔP_(s) and the actually measured pressure value of thesecond press cylinder 42 a. Each of the actually measured pressure valueof the first press cylinder 41 a and the actually measured pressurevalue of the second press cylinder 42 a can be estimated according to,for example, a measurement value of a valve opening meter.

The press pressure deviation calculator 817 c supplies the calculatedpressure deviation of the first press cylinder 41 a and the calculatedpressure deviation of the second press cylinder 42 a to the PIDcontroller 817 b. The PID controller 817 b generates a pressureoperation amount of the first press cylinder 41 a and a pressureoperation amount of the second press cylinder 42 a, on the basis of thepressure deviation of the first press cylinder 41 a and the pressuredeviation of the second press cylinder 42 a.

Note that, instead of PID compensation, P compensation, PI compensation,or PD compensation may be used. In the P compensation, a proportionalterm (stationary deviation) can be controlled, in the I compensation, anintegral term can be controlled, and in the D compensation, adifferential term can be controlled.

The PID controller 817 b supplies the generated pressure operationamount of the first press cylinder 41 a and the generated pressureoperation amount of the second press cylinder 42 a to the press pressurecontroller 817 a. The press pressure controller 817 a includes anactuator and drives each of the first press cylinder 41 a and the secondpress cylinder 42 a on the basis of the pressure operation amount of thefirst press cylinder 41 a and the pressure operation amount of thesecond press cylinder 42 a.

The bend pressure deviation calculator 818 c calculates a deviationbetween the corrected driving-side bend pressure setting valueB_(m)+ΔB_(m) supplied from the setting value corrector 816 and theactually measured pressure value of the first bend cylinder 51 a and adeviation between the corrected operation-side bend pressure settingvalue B_(s)+ΔB_(s) and the actually measured pressure value of thesecond bend cylinder 52 a.

The bend pressure deviation calculator 818 c supplies the calculatedpressure deviation of the first bend cylinder 51 a and the calculatedpressure deviation of the second bend cylinder 52 a to the PIDcontroller 818 b. The PID controller 818 b generates the pressureoperation amount of the first bend cylinder 51 a and the pressureoperation amount of the second bend cylinder 52 a, on the basis of thepressure deviation of the first bend cylinder 51 a and the pressuredeviation of the second bend cylinder 52 a.

The PID controller 818 b supplies the generated pressure operationamount of the first bend cylinder 51 a and the generated pressureoperation amount of the second bend cylinder 52 a to the bend pressurecontroller 818 a. The bend pressure controller 818 a includes anactuator and drives each of the first bend cylinder 51 a and the secondbend cylinder 52 a on the basis of the pressure operation amount of thefirst bend cylinder 51 a and the pressure operation amount of the secondbend cylinder 52 a.

As described above, in the feedback control example 1, the feedbackcontrol is performed such that the pressure of the press cylindermaintains the setting value. The operation target is the pressure of thepress cylinder. In addition, the feedback control is performed such thatthe pressure of the bend cylinder maintains the setting value. Theoperation target is the pressure of the bend cylinder. The thickness ofthe electrode plate 2 is controlled to the target value by adding thecorrection value calculated from the thickness measurement value to thesetting value of the press cylinder pressure and the setting value ofthe bend cylinder pressure.

FIG. 6 is a diagram illustrating a feedback control example 2 using thefirst control panel 81 and the second control panel 82. The feedbackcontrol example 2 is control used in the roll press device according tothe second embodiment illustrated in FIG. 2 . In the feedback controlexample 2, the first press cylinder 41 a and the second press cylinder42 a are used as the compression mechanism. As the bend mechanism, atleast one of the third bend cylinder 51 b or the fifth bend cylinder 51c and at least one of the fourth bend cylinder 52 b or the sixth bendcylinder 52 c are used. Hereinafter, differences from the feedbackcontrol example 1 illustrated in FIG. 5 will be described. In thefeedback control example 2, instead of the press pressure controller 817a, the PID controller 817 b, and the press pressure deviation calculator817 c, a cylinder position controller 817 d, a PID controller 817 e, anda cylinder position deviation calculator 817 f are provided.

According to experiments by the present inventors, it has been foundthat there are relations defined by the following (Formula 16) to(Formula 18) between the first feature amount T_(t−m), the secondfeature amount T_(t−s), and the third feature amount T_(drop) and thedriving-side press cylinder position G_(m), the operation-side presscylinder position G_(s), and the average press cylinder positionG_(ave)=(G_(m)+G_(s))/2.

T _(t−n) ∝G _(m)  (Formula 16)

T _(t−s) ∝G _(s)  (Formula 17)

T _(drop) ∝−G _(ave)  (Formula 18)

The thickness of the electrode plate 2 does not increase or decreaseonly by a change in the press cylinder position, and it is necessary toconsider elastic deformation amounts of the first pressure roller 11 andthe second pressure roller 12 due to a change in the reaction force fromthe electrode plate 2.

The correlation between the driving-side press cylinder position G_(m),the operation-side press cylinder position G_(s), and the average presscylinder position G_(ave) and the first feature amount T_(t−m), thesecond feature amount T_(t−s), and the third feature amount T_(drop)representing the thickness of the electrode plate 2 is experimentallyobtained in advance.

When the pressure difference between the driving-side bend pressureB_(m) and the operation-side bend pressure B_(s) is caused to beconstant, a driving-side press cylinder position correction value ΔG_(m)and an operation-side press cylinder position correction value ΔG_(s) ofthe driving-side press cylinder position G_(m) and the operation-sidepress cylinder position G_(s) at which the first feature amount T_(t−m)and the second feature amount T_(t−s) become zero at the same time areobtained from the correlations shown in the above (Formula 16) and(Formula 17).

From the correlation shown in the above (Formula 18), a change amountΔT_(drop) of the third feature amount T_(drop) associated with thecorrection of the driving-side press cylinder position G_(m) and theoperation-side press cylinder position G_(s) described above isobtained. From the correlation shown in the above (Formula 14), acorrection value ΔB_(ave) of the average bend pressure B_(ave) forcausing the third feature amount T_(drop)+ΔT_(drop) to which the changeamount ΔT_(drop) has been added to be zero is obtained.

The thickness over the entire width of the electrode plate 2 can becontrolled to the target value T_(t) by controlling the cylinderpositions of the first press cylinder 41 a and the second press cylinder42 a and the pressures of the third bend cylinder 51 b, the fifth bendcylinder 51 c, the fourth bend cylinder 52 b, and the sixth bendcylinder 52 c such that the cylinder position of the first presscylinder 41 a becomes the corrected driving-side press cylinder positionsetting value G_(m)+ΔG_(m), the cylinder position of the second presscylinder 42 a becomes the corrected operation-side press cylinderposition setting value G_(s)+ΔG_(s), the pressures of the third bendcylinder 51 b and the fifth bend cylinder 51 c become the correcteddriving-side bend pressure setting value B_(m)+ΔB_(m), and the pressuresof the fourth bend cylinder 52 b and the sixth bend cylinder 52 c becomethe corrected operation-side bend pressure setting value B_(s)+ΔB_(s).

The correction value calculator 815 is supplied with the first featureamount T_(t−m), the second feature amount T_(t−s), and the third featureamount T_(drop) from the feature amount calculator 814. In addition, thedriving-side press cylinder position setting value G_(m), theoperation-side press cylinder position setting value G_(s), thedriving-side bend pressure setting value B_(m), and the operation-sidebend pressure setting value B_(s) input by the operator via the HMI aresupplied. The values derived in advance are set to the driving-sidepress cylinder position setting value G_(m), the operation-side presscylinder position setting value G_(s), the driving-side bend pressuresetting value B_(m), and the operation-side bend pressure setting valueB_(s) such that all of the first feature amount T_(t−m), the secondfeature amount T_(t−s), and the third feature amount T_(drop) becomezero under the standard condition.

The correction value calculator 815 calculates the driving-side presscylinder position correction value ΔG_(m), the operation-side presscylinder position correction value ΔG_(s), the driving-side bendpressure correction value ΔB_(m), and the operation-side bend pressurecorrection value ΔB_(s), on the basis of the first feature amountT_(t−m), the second feature amount T_(t−s), the third feature amountT_(drop), and proportional constants of the above (Formula 16), (Formula17), (Formula 18), and (Formula 14). The correction value calculator 815supplies the calculated driving-side press cylinder position correctionvalue ΔG_(m), operation-side press cylinder position correction valueΔG_(s), driving-side bend pressure correction value ΔB_(m), andoperation-side bend pressure correction value ΔB_(s) to the settingvalue corrector 816.

The setting value corrector 816 is supplied with the driving-side presscylinder position correction value ΔG_(m), the operation-side presscylinder position correction value ΔG_(s), the driving-side bendpressure correction value ΔB_(m), and the operation-side bend pressurecorrection value ΔB_(s) from the correction value calculator 815. Inaddition, the driving-side press cylinder position setting value G_(m),the operation-side press cylinder position setting value G_(s), thedriving-side bend pressure setting value B_(m), and the operation-sidebend pressure setting value B_(s) input by the operator via the HMI aresupplied.

The setting value corrector 816 adds the driving-side press cylinderposition correction value ΔG_(m), the operation-side press cylinderposition correction value ΔG_(s), the driving-side bend pressurecorrection value ΔB_(m), and the operation-side bend pressure correctionvalue ΔB_(s) to the driving-side press cylinder position setting valueG_(m), the operation-side press cylinder position setting value G_(s),the driving-side bend pressure setting value B_(m), and theoperation-side bend pressure setting value B_(s), respectively, andcalculates the corrected driving-side press cylinder position settingvalue G_(m)+ΔG_(m), the corrected operation-side press cylinder positionsetting value G_(s)+ΔG_(s), the corrected driving-side bend pressuresetting value B_(m)+ΔB_(m), and the corrected operation-side bendpressure setting value B_(s)+ΔB_(s).

The setting value corrector 816 supplies the calculated correcteddriving-side press cylinder position setting value G_(m)+ΔG_(m) andcorrected operation-side press cylinder position setting valueG_(s)+ΔG_(s) to the cylinder position deviation calculator 817 f, andsupplies the corrected driving-side bend pressure setting valueB_(m)+ΔB_(m) and the corrected operation-side bend pressure settingvalue B₃+ΔB_(s) to the bend pressure deviation calculator 818 c.

The cylinder position deviation calculator 817 f calculates a deviationbetween the corrected driving-side press cylinder position setting valueG_(m)+ΔG_(m) supplied from the setting value corrector 816 and theactual measurement value of the cylinder position of the first presscylinder 41 a measured by the first magnescale 41 c. In addition, thecylinder position deviation calculator 817 f calculates a deviationbetween the corrected operation-side press cylinder position settingvalue G_(s)+ΔG_(s) supplied from the setting value corrector 816 and theactual measurement value of the cylinder position of the second presscylinder 42 a measured by the second magnescale 42 c.

The cylinder position deviation calculator 817 f supplies the calculatedcylinder position deviation of the first press cylinder 41 a and thecalculated cylinder position deviation of the second press cylinder 42 ato the PID controller 817 e. The PID controller 817 e generates thepressure operation amount of the first press cylinder 41 a and thepressure operation amount of the second press cylinder 42 a, on thebasis of the cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42 a.

The PID controller 817 e supplies the generated pressure operationamount of the first press cylinder 41 a and the generated pressureoperation amount of the second press cylinder 42 a to the cylinderposition controller 817 d. The cylinder position controller 817 dincludes an actuator and drives each of the first press cylinder 41 aand the second press cylinder 42 a on the basis of the pressureoperation amount of the first press cylinder 41 a and the pressureoperation amount of the second press cylinder 42 a.

In the feedback control example 2, the third bend cylinder 51 b, thefifth bend cylinder 51 c, the fourth bend cylinder 52 b, and the sixthbend cylinder 52 c are controlled as the bend mechanism. Since this isbasically the same as the case of controlling the first bend cylinder 51a and the second bend cylinder 52 a in the feedback control example 1,the description thereof is omitted.

As described above, in the feedback control example 2, the feedbackcontrol is performed such that the position of the press cylindermaintains the setting value instead of performing the feedback controlsuch that the pressure of the press cylinder maintains the setting valueas in the feedback control example 1. The operation target is theposition of the press cylinder. Even in the feedback control example 2,the feedback control is performed such that the pressure of the bendcylinder maintains the setting value. The operation target is thepressure of the bend cylinder. The thickness of the electrode plate 2 iscontrolled to the target value by adding the correction value calculatedfrom the thickness measurement value to the setting value of the presscylinder position and the setting value of the bend cylinder pressure.

FIG. 7 is a diagram illustrating a feedback control example 3 using thefirst control panel 81 and the second control panel 82. The feedbackcontrol example 3 is control used in the roll press device according tothe first embodiment illustrated in FIG. 1 . In the feedback controlexample 3, the first electric screw 41 b and the second electric screw42 b are used as the compression mechanism. Note that a sufficientlylarge pressure (fixed value) is applied to the first press cylinder 41 aand the second press cylinder 42 a such that the position of thecylinder is not changed by position control of the first electric screw41 b and the second electric screw 42 b.

The first bend cylinder 51 a and the second bend cylinder 52 a are usedas the bend mechanism. Hereinafter, differences from the feedbackcontrol example 1 illustrated in FIG. 5 will be described. In thefeedback control example 3, instead of the press pressure controller 817a, the PID controller 817 b, and the press pressure deviation calculator817 c, a screw position controller 817 g, a PID controller 817 h, and ascrew position deviation calculator 817 i are provided.

According to experiments by the present inventors, it has been foundthat there are relations defined by the following (Formula 19) to(Formula 21) between the first feature amount T_(t−m), the secondfeature amount T_(t−s), and the third feature amount T_(drop) and thedriving-side electric screw position D_(m), the operation-side electricscrew position D_(s), and the average electric screw positionD_(ave)=(D_(m)+D_(s))/2.

T _(t−n) ∝D _(m)  (Formula 19)

T _(t−s) ∝D _(s)  (Formula 20)

T _(drop) ∝−D _(ave)  (Formula 21)

The thickness of the electrode plate 2 does not increase or decreaseonly by the change in the electric screw position, and it is necessaryto consider elastic deformation amounts of the first pressure roller 11and the second pressure roller 12 due to the change in the reactionforce from the electrode plate 2.

The correlation between the driving-side electric screw position D_(m),the operation-side electric screw position D_(s), and the averageelectric screw position D_(ave) and the first feature amount T_(t−m),the second feature amount T_(t−s), and the third feature amount T_(drop)representing the thickness of the electrode plate 2 is experimentallyobtained in advance.

In a case where the pressure difference between the driving-side bendpressure B_(m) and the operation-side bend pressure B_(s) is caused tobe constant when the preload pressure is constant or when the preloadmechanism is not provided, a driving-side electric screw positioncorrection value ΔD_(m) and an operation-side electric screw positioncorrection value ΔD_(s) of the driving-side electric screw positionD_(m) and the operation-side electric screw position D_(s) at which thefirst feature amount T_(t−m) and the second feature amount T_(t−s)become zero at the same time are obtained from the correlations shown inthe above (Formula 19) and (Formula 20)

From the correlation shown in the above (Formula 21), a change amountΔT_(drop) of the third feature amount T_(drop) associated with thecorrection of the driving-side electric screw position D_(m) and theoperation-side electric screw position D_(s) described above isobtained. From the correlation shown in the above (Formula 14), acorrection value ΔB_(ave) of the average bend pressure B_(ave) forcausing the third feature amount T_(drop)+ΔT_(drop) to which the changeamount ΔT_(drop) has been added to be zero is obtained.

The thickness over the entire width of the electrode plate 2 can becontrolled to the target value T_(t) by controlling the positions of thefirst electric screw 41 b and the second electric screw 42 b and thepressures of the first bend cylinder 51 a and the second bend cylinder52 a such that the position of the first electric screw 41 b becomes acorrected driving-side electric screw position setting valueD_(m)+ΔD_(m), the position of the second electric screw 42 b becomes acorrected operation-side electric screw position setting valueD_(s)+ΔD_(s), the pressure of the first bend cylinder 51 a becomes acorrected driving-side bend pressure setting value B_(m)+ΔB_(m), and thepressure of the second bend cylinder 52 a becomes a correctedoperation-side bend pressure setting value B_(s)+ΔB_(s), respectively.

The correction value calculator 815 is supplied with the first featureamount T_(t−m), the second feature amount T_(t−s), and the third featureamount T_(drop) from the feature amount calculator 814. In addition, thedriving-side electric screw position setting value D_(m), theoperation-side electric screw position setting value D_(s), thedriving-side bend pressure setting value B_(m), and the operation-sidebend pressure setting value B_(s) input by the operator via the HMI aresupplied. The values derived in advance are set to the driving-sideelectric screw position setting value D_(m), the operation-side electricscrew position setting value D_(s), the driving-side bend pressuresetting value B_(m), and the operation-side bend pressure setting valueB_(s) such that all of the first feature amount T_(t−m), the secondfeature amount T_(t−s), and the third feature amount T_(drop) becomezero under the standard condition.

The correction value calculator 815 calculates the driving-side electricscrew position correction value ΔD_(m), the operation-side electricscrew position correction value ΔD_(s), the driving-side bend pressurecorrection value ΔB_(m), and the operation-side bend pressure correctionvalue ΔB_(s), on the basis of the first feature amount T_(t−m), thesecond feature amount T_(t−s), the third feature amount T_(drop), andproportional constants of the above (Formula 19), (Formula 20), (Formula21), and (Formula 14). The correction value calculator 815 supplies thecalculated driving-side electric screw position correction value ΔD_(m),operation-side electric screw position correction value ΔD_(s),driving-side bend pressure correction value ΔB_(m), and operation-sidebend pressure correction value ΔB_(s) to the setting value corrector816.

The setting value corrector 816 is supplied with the driving-sideelectric screw position correction value ΔD_(m), the operation-sideelectric screw position correction value ΔD_(s), the driving-side bendpressure correction value ΔB_(m), and the operation-side bend pressurecorrection value ΔB_(s) from the correction value calculator 815. Inaddition, the driving-side electric screw position setting value D_(m),the operation-side electric screw position setting value D_(s), thedriving-side bend pressure setting value B_(m), and the operation-sidebend pressure setting value B_(s) input by the operator via the HMI aresupplied.

The setting value corrector 816 adds the driving-side electric screwposition correction value ΔD_(m), the operation-side electric screwposition correction value ΔD_(s), the driving-side bend pressurecorrection value ΔB_(m), and the operation-side bend pressure correctionvalue ΔB_(s) to the driving-side electric screw position setting valueD_(m), the operation-side electric screw position setting value D_(s),the driving-side bend pressure setting value B_(m), and theoperation-side bend pressure setting value B_(s), respectively, andcalculates the corrected driving-side electric screw position settingvalue D_(m)+ΔD_(m), the corrected operation-side electric screw positionsetting value D_(s)+ΔD_(s), the corrected driving-side bend pressuresetting value B_(m)+ΔB_(m), and the corrected operation-side bendpressure setting value B_(s)+ΔB_(s).

The setting value corrector 816 supplies the calculated correcteddriving-side electric screw position setting value D_(m)+ΔD_(m) andcorrected operation-side electric screw position setting valueD_(s)+ΔD_(s) to the screw position deviation calculator 817 i, andsupplies the corrected driving-side bend pressure setting valueB_(m)+ΔB_(m) and the corrected operation-side bend pressure settingvalue B_(s)+ΔB_(s) to the bend pressure deviation calculator 818 c.

The screw position deviation calculator 817 i calculates a deviationbetween the corrected driving-side electric screw position setting valueD_(m)+ΔD_(m) supplied from the setting value corrector 816 and themeasurement value of the position of the first electric screw 41 b. Inaddition, the screw position deviation calculator 817 i calculates adeviation between the corrected operation-side electric screw positionsetting value D_(s)+ΔD_(s) supplied from the setting value corrector 816and the measurement value of the position of the second electric screw42 b.

The screw position controller 817 g includes servo motors for reducingthe pressures of the first electric screw 41 b and the second electricscrew 42 b, respectively. A position change amount of each of the firstelectric screw 41 b and the second electric screw 42 b can be calculatedfrom the rotation speed of each servomotor.

The screw position deviation calculator 817 i supplies the calculatedposition deviation of the first electric screw 41 b and the calculatedposition deviation of the second electric screw 42 b to the PIDcontroller 817 h. The PID controller 817 h generates a rotationoperation amount of the servomotor for the first electric screw 41 b anda rotation operation amount of the servomotor for the second electricscrew 42 b, on the basis of the position deviation of the first electricscrew 41 b and the position deviation of the second electric screw 42 b.

The PID controller 817 h supplies the generated rotation operationamount of the servomotor for the first electric screw 41 b and thegenerated rotation operation amount of the servomotor for the secondelectric screw 42 b to the screw position controller 817 g. The screwposition controller 817 g drives each of the servomotor for the firstelectric screw 41 b and the servomotor for the second electric screw 42b, on the basis of the rotation operation amount of the servomotor forthe first electric screw 41 b and the rotation operation amount of theservomotor for the second electric screw 42 b.

As described above, in the feedback control example 3, the feedbackcontrol is performed such that the position of the electric screwmaintains the setting value instead of performing the feedback controlsuch that the pressure of the press cylinder maintains the setting valueas in the feedback control example 1. The operation target is therotation speed of the servo motor. Even in the feedback control example3, the feedback control is performed such that the pressure of the bendcylinder maintains the setting value. The operation target is thepressure of the bend cylinder. The thickness of the electrode plate 2 iscontrolled to the target value by adding the correction value calculatedfrom the thickness measurement value to the setting value of theposition of the electric screw and the setting value of the bendcylinder pressure.

FIG. 8 is a diagram illustrating a feedback control example 4 using thefirst control panel 81 and the second control panel 82. The feedbackcontrol example 4 is control used in the roll press device according tothe third embodiment illustrated in FIG. 3 . In the feedback controlexample 4, the first electric cotter 41 e and the second electric cotter42 e are used as the compression mechanism. Note that a sufficientlylarge pressure (fixed value) is applied to the first press cylinder 41 aand the second press cylinder 42 a such that the position of thecylinder is not changed by the height control of the first electriccotter 41 e and the second electric cotter 42 e.

As the bend mechanism, at least one of the third bend cylinder 51 b orthe fifth bend cylinder 51 c and at least one of the fourth bendcylinder 52 b or the sixth bend cylinder 52 c are used. Hereinafter,differences from the feedback control example 1 illustrated in FIG. 5will be described. In the feedback control example 4, instead of thepress pressure controller 817 a, the PID controller 817 b, and the presspressure deviation calculator 817 c, a cotter height controller 817 j, aPID controller 817 k, and a cotter height deviation calculator 817 l areprovided.

In a state where the first electric cotter 41 e and the second electriccotter 42 e are in contact with the first press cylinder 41 a and thesecond press cylinder 42 a, and the first pressure roller 11 and thesecond pressure roller 12 are in contact with the electrode plate 2, apart of the press load by the first press cylinder 41 a and the secondpress cylinder 42 a is dispersed in the first electric cotter 41 e andthe second electric cotter 42 e, so that (load acting on the electrodeplate 2) is represented by (press load) −(load acting on the cotter).

When the pressures of the first press cylinder 41 a and the second presscylinder 42 a are constant, the press load is constant. In this state,the load acting on the electrode plate 2 can be changed by changing thecotter height to change the load acting on the cotter. It is difficultto measure a change in load acting on each of the first electric cotter41 e and the second electric cotter 42 e due to a change in height ofeach of the first electric cotter 41 e and the second electric cotter 42e.

According to experiments by the present inventors, it has been foundthat there are relations defined by the following (Formula 22) to(Formula 24) between the first feature amount T_(t−m), the secondfeature amount T_(t−s), and the third feature amount T_(drop) and thedriving-side electric cotter height K_(m), the operation-side electriccotter height K_(s), and the average electric cotter heightK_(ave)=(K_(m)+K_(s))/2.

T _(t−n) ∝K _(m)  (Formula 22)

T _(t−s) ∝K _(s)  (Formula 23)

T _(drop) ∝−K _(ave)  (Formula 24)

The correlation between the driving-side electric cotter height K_(m),the operation-side electric cotter height K_(s), and the averageelectric cotter height K_(ave) and the first feature amount T_(t−m), thesecond feature amount T_(t−s), and the third feature amount T_(drop)representing the thickness of the electrode plate 2 is experimentallyobtained in advance.

When the pressure difference between the driving-side bend pressureB_(m) and the operation-side bend pressure B_(s) is caused to beconstant, a driving-side electric cotter height correction value ΔK_(m)and an operation-side electric cotter height correction value ΔK_(s) ofthe driving-side electric cotter height K_(m) and the operation-sideelectric cotter height K_(s) at which the first feature amount T_(t−m)and the second feature amount T_(t−s) become zero at the same time areobtained from the correlations shown in the above (Formula 22) and(Formula 23).

From the correlation shown in the above (Formula 24), a change amountΔT_(drop) of the third feature amount T_(drop) associated with thecorrection of the driving-side electric cotter height K_(m) and theoperation-side electric cotter height K_(s) described above is obtained.From the correlation shown in the above (Formula 14), a correction valueΔB_(ave) of the average bend pressure B_(ave) for causing the thirdfeature amount T_(drop)+ΔT_(drop) to which the change amount ΔT_(drop)has been added to be zero is obtained.

The thickness over the entire width of the electrode plate 2 can becontrolled to the target value T_(t) by controlling the heights of thefirst electric cotter 41 e and the second electric cotter 42 e and thepressures of the third bend cylinder 51 b, the fifth bend cylinder 51 c,the fourth bend cylinder 52 b, and the sixth bend cylinder 52 c suchthat the height of the first electric cotter 41 e becomes a correcteddriving-side electric cotter height setting value K_(m)+ΔK_(m), theheight of the second electric cotter 42 e becomes a correctedoperation-side electric cotter height setting value K_(s)+ΔK_(s), thepressures of the third bend cylinder 51 b and the fifth bend cylinder 51c become a corrected driving-side bend pressure setting valueB_(m)+ΔB_(m), and the pressures of the fourth bend cylinder 52 b and thesixth bend cylinder 52 c becomes a corrected operation-side bendpressure setting value B_(s)+ΔB_(s).

The correction value calculator 815 is supplied with the first featureamount T_(t−m), the second feature amount T_(t−s), and the third featureamount T_(drop) from the feature amount calculator 814. In addition, thedriving-side electric cotter height setting value K_(m), theoperation-side electric cotter height setting value K_(s), thedriving-side bend pressure setting value B_(m), and the operation-sidebend pressure setting value B_(s) input by the operator via the HMI aresupplied. The values derived in advance are set to the driving-sideelectric cotter height setting value K_(m), the operation-side electriccotter height setting value K_(s), the driving-side bend pressuresetting value B_(m), and the operation-side bend pressure setting valueB_(s) such that all of the first feature amount T_(t−m), the secondfeature amount T_(t−s), and the third feature amount T_(drop) becomezero under the standard condition.

The correction value calculator 815 calculates the driving-side electriccotter height correction value ΔK_(m), the operation-side electriccotter height correction value ΔK_(s), the driving-side bend pressurecorrection value ΔB_(m), and the operation-side bend pressure correctionvalue ΔB_(s), on the basis of the first feature amount T_(t−m), thesecond feature amount T_(t−s), the third feature amount T_(drop), andproportional constants of the above (Formula 22), (Formula 23), (Formula24), and (Formula 14). The correction value calculator 815 supplies thecalculated driving-side electric cotter height correction value ΔK_(m),operation-side electric cotter height correction value ΔK_(s),driving-side bend pressure correction value ΔB_(m), and operation-sidebend pressure correction value ΔB_(s) to the setting value corrector816.

The setting value corrector 816 is supplied with the driving-sideelectric cotter height correction value ΔK_(m), the operation-sideelectric cotter height correction value ΔK_(s), the driving-side bendpressure correction value ΔB_(m), and the operation-side bend pressurecorrection value ΔB_(s) from the correction value calculator 815. Inaddition, the driving-side electric cotter height setting value K_(m),the operation-side electric cotter height setting value K_(s), thedriving-side bend pressure setting value B_(m), and the operation-sidebend pressure setting value B_(s) input by the operator via the HMI aresupplied.

The setting value corrector 816 adds the driving-side electric cotterheight correction value ΔK_(m), the operation-side electric cotterheight correction value ΔK_(s), the driving-side bend pressurecorrection value ΔB_(m), and the operation-side bend pressure correctionvalue ΔB_(s) to the driving-side electric cotter height setting valueK_(m), the operation-side electric cotter height setting value K_(s),the driving-side bend pressure setting value B_(m), and theoperation-side bend pressure setting value B_(s), respectively, andcalculates the corrected driving-side electric cotter height settingvalue K_(m)+ΔK_(m), the corrected operation-side electric cotter heightsetting value K₃+ΔK_(s), the corrected driving-side bend pressuresetting value B_(m)+ΔB_(m), and the corrected operation-side bendpressure setting value B₃+ΔB_(s).

The setting value corrector 816 supplies the calculated correcteddriving-side electric cotter height setting value K_(m)+ΔK_(m) andcorrected operation-side electric cotter height setting valueK_(s)+ΔK_(s) to the cotter height deviation calculator 817 l, andsupplies the corrected driving-side bend pressure setting valueB_(m)+ΔB_(m) and the corrected operation-side bend pressure settingvalue B₃+ΔB_(s) to the bend pressure deviation calculator 818 c.

The cotter height deviation calculator 817 l calculates a deviationbetween the corrected driving-side electric cotter height setting valueK_(m)+ΔK_(m) supplied from the setting value corrector 816 and themeasurement value of the height of the first electric cotter 41 e. Inaddition, the cotter height deviation calculator 817 l calculates adeviation between the corrected operation-side electric cotter heightsetting value K₃+ΔK_(s) supplied from the setting value corrector 816and the measurement value of the height of the second electric cotter 42e.

The cotter height controller 817 j includes linear servo motors forsliding the lower cotters of the first electric cotter 41 e and thesecond electric cotter 42 e in the left-right direction. The heightchange amount of each of the first electric cotter 41 e and the secondelectric cotter 42 e can be calculated from the movement amount of eachlinear servo motor. Note that a distance meter may be provided betweenthe first main bearing 21 and the third main bearing 23 to measure theheight of the first electric cotter 41 e, and a distance meter may beprovided between the second main bearing 22 and the fourth main bearing24 to measure the height of the second electric cotter 42 e.

The cotter height deviation calculator 817 l supplies the calculatedheight deviation of the first electric cotter 41 e and the calculatedheight deviation of the second electric cotter 42 e to the PIDcontroller 817 k. The PID controller 817 k generates a movementoperation amount of the linear servo motor for the first electric cotter41 e and a movement operation amount of the linear servo motor for thesecond electric cotter 42 e, on the basis of the height deviation of thefirst electric cotter 41 e and the height deviation of the secondelectric cotter 42 e.

The PID controller 817 k supplies the generated movement operationamount of the linear servo motor for the first electric cotter 41 e andthe generated movement operation amount of the linear servo motor forthe second electric cotter 42 e to the cotter height controller 817 j.The cotter height controller 817 j drives the linear servo motor for thefirst electric cotter 41 e and the linear servo motor for the secondelectric cotter 42 e, on the basis of the movement operation amount ofthe linear servo motor for the first electric cotter 41 e and themovement operation amount of the linear servo motor for the secondelectric cotter 42 e.

In the feedback control example 4, the third bend cylinder 51 b, thefifth bend cylinder 51 c, the fourth bend cylinder 52 b, and the sixthbend cylinder 52 c are controlled as the bend mechanism. Since this isbasically the same as the case of controlling the first bend cylinder 51a and the second bend cylinder 52 a in the feedback control example 1,the description thereof is omitted.

As described above, in the feedback control example 4, the feedbackcontrol is performed such that the height of the electric cottermaintains the setting value instead of performing the feedback controlsuch that the pressure of the press cylinder maintains the setting valueas in the feedback control example 1. The operation target is themovement amount of the linear servo motor. Even in the feedback controlexample 4, the feedback control is performed such that the pressure ofthe bend cylinder maintains the setting value. The operation target isthe pressure of the bend cylinder. The thickness of the electrode plate2 is controlled to the target value by adding the correction valuecalculated from the thickness measurement value to the setting value ofthe height of the electric cotter and the setting value of the bendcylinder pressure.

When a hydraulic cylinder is used for the first press cylinder 41 a, thesecond press cylinder 42 a, the first bend cylinder 51 a, the secondbend cylinder 52 a, the third bend cylinder 51 b, the fourth bendcylinder 52 b, the fifth bend cylinder 51 c, and the sixth bend cylinder52 c described above, it is desirable to install a hydraulic controldevice as close as possible to the hydraulic cylinder. In addition, itis desirable to use a hydraulic servo valve having a high pressurecontrol speed as the hydraulic control device. As a result, it ispossible to prevent the delay of the pressure response and the pressurehunting caused by the pressure change of the hydraulic pipe due to thepressure change of the hydraulic cylinder.

Incidentally, in the method for measuring the thickness of the electrodeplate 2 during being conveyed by the thickness meter 70 and correctingthe thickness of the electrode plate 2 by the feedback control describedin the feedback control examples 1 to 4, it is difficult to correct thethickness change at the time of acceleration or deceleration of theconveyance line with high accuracy. It is also conceivable to decreasethe speed at the time of acceleration or deceleration of the conveyanceline, but in this case, production efficiency is lowered. Therefore, amethod for predicting the thickness change of the electrode plate 2 dueto the speed change of the conveyance line and correcting the thicknessof the electrode plate 2 by feedforward control is introduced.

FIG. 9 is a diagram plotting a relation between a change in line speedand a change in thickness of the electrode plate 2 under a constantpress-bend condition in the certain roll press device 1. A horizontalaxis represents a line speed [mpm], and a vertical axis represents athickness-width average value [μm] of the electrode plate 2. Asillustrated in FIG. 9 , it can be seen that the thickness of theelectrode plate 2 increases as the line speed increases.

FIG. 10 is a diagram illustrating a feedforward control example 1 usingthe first control panel 81. The feedforward control example 1 is controlused in the roll press device according to the first embodimentillustrated in FIG. 1 . In the feedforward control example 1, the firstpress cylinder 41 a and the second press cylinder 42 a are used as thecompression mechanism. In the present specification, in order tosimplify the feedforward control, the bend mechanism is not used for thefeedforward control.

FIG. 10 illustrates functional blocks realized by the first controlpanel 81 related to the feedforward control example 1. The first controlpanel 81 includes a line speed setting changer 819, a line speedcontroller 8110, a correction value calculator 815, a setting valuecorrector 816, a press pressure controller 817 a, a PID controller 817b, and a press pressure deviation calculator 817 c.

The line speed controller 8110 controls the rotation speed of theunwinder 13, the rotation speeds of the first pressure roller 11 and thesecond pressure roller 12, and the rotation speed of the winder 14, onthe basis of a command value of the line speed supplied from the linespeed setting changer 819.

The line speed set by the operator is input to the line speed settingchanger 819. The acceleration at the time of acceleration and thedeceleration at the time of deceleration of the conveyance line arebasically set in advance by the manufacturer of the roll press device 1.Note that the acceleration at the time of acceleration and thedeceleration at the time of deceleration may be specifications that canbe set and changed by the user.

In the feedforward control example 1, a thickness change of theelectrode plate 2 due to a change in line speed is predicted, a pressload necessary for maintaining the thickness of the electrode plate 2constantly is calculated, and the press load is changed by feedforwardcontrol. By experimentally investigating the relation between the linespeed and the thickness of the electrode plate 2, an appropriate presspressure can be predicted with high accuracy.

When the acceleration or deceleration of the line speed is a [m/s²], theline speed V_(s) after S seconds from the start of acceleration ordeceleration can be defined as the following (Formula 25) by using aspeed V₀ at the start of acceleration or deceleration and a changeamount ΔV_(s) of the line speed after S seconds from the start ofacceleration or deceleration. The change amount ΔV_(s) of the line speedafter S seconds from the start of acceleration or deceleration can bedefined as the following (Formula 26).

V _(s) =V ₀ +ΔV _(s) =V ₀ +α×S  (Formula 25)

ΔV _(s) =V _(s) −V ₀ =α×S  (Formula 26)

As illustrated in FIG. 9 , the change amount ΔV_(s) of the line speedafter S seconds and the change amount ΔT_(ave) of the thickness averagevalue T_(ave) in the width direction of the electrode plate 2 are in aproportional relation, so that a relation of the following (Formula 27)holds.

ΔT _(ave) =D×ΔV _(s)  (Formula 27)

D is a proportional constant.

The relation between the change amount ΔV of the line speed and thechange amount ΔT_(ave) of the thickness average value T_(ave) may beexperimentally obtained and fitted with a multidimensional function, anexponential function, or a logarithmic function.

In addition, since the average value L_(ave) (hereinafter, referred toas a linear pressure) of the press load acting on the electrode plate 2in the width direction and the thickness average value T_(ave) afterpressing are in a proportional relation, a relation of the following(Formula 28) holds between the change amount ΔL_(ave) of the linearpressure and the change amount ΔT_(ave) of the thickness average valueT_(ave) when the linear pressure is changed.

ΔT _(ave) =E×ΔL _(ave)  (Formula 28)

E is a proportional constant.

The correction value ΔL_(ave,s) of the linear pressure for causing thechange amount ΔT_(ave,s) of the thickness average value T_(ave) after Sseconds from the start of acceleration or deceleration to be zero can beobtained by the following (Formula 29) after removing ΔV_(s) andΔT_(ave) from the relations of the above (Formula 26), (Formula 27), and(Formula 28).

ΔL _(ave,s)={(D×α)/E}×S  (Formula 29)

When the linear pressure at the time of acceleration or deceleration isL_(ave,0), the thickness change of the electrode plate 2 due to thechange in the line speed can be reduced by feedforward-controlling thepress mechanism such that the linear pressure after S seconds becomesL_(ave,0)+ΔL_(ave,s).

In the feedforward control example 1, by causing the positions of thefirst electric screw 41 b and the second electric screw 42 b to beconstant and changing the pressures of the first press cylinder 41 a andthe second press cylinder 42 a, the press load acting on the electrodeplate 2 is changed. Since there is a proportional relation between thechange amount ΔP_(ave) of the average press pressureP_(ave)=(P_(m)+P_(s))/2 of the driving-side press pressure P_(m) and theoperation-side press pressure P_(s) and the change amount ΔT_(ave) ofthe thickness average value T_(ave) of the electrode plate 2, a relationof the following (Formula 30) holds between the change amount ΔP_(ave)of the average press pressure P_(ave) and the change amount ΔT_(ave) ofthe thickness average value T_(ave) when the press pressure is changed.

ΔT _(ave) =F×ΔP _(ave)  (Formula 30)

F is a proportional constant.

The correction value ΔP_(ave,s) of the average press pressure P_(ave)for causing the change amount ΔT_(ave,s) of the thickness average valueT_(ave) after S seconds from the start of acceleration or decelerationto be zero can be obtained by the following (Formula 31) after removingΔV_(s) and ΔT_(ave) from the relations of the above (Formula 26),(Formula 27), and (Formula 30).

ΔP _(ave,s)={(D×α)/F}×S  (Formula 31)

When the average press pressure at the time of acceleration ordeceleration is P_(ave,0), the pressures of the first press cylinder 41a and the second press cylinder 42 a are feedforward-controlled suchthat the average press pressure after S seconds becomesP_(ave,0)+ΔP_(ave,s). As a result, the thickness change of the electrodeplate 2 due to the change in the line speed can be suppressed.

A differential pressure between the driving-side press pressure P_(m)and the operation-side press pressure P_(s) during an accelerationperiod or a deceleration period of the conveyance line may be basicallythe same as that before the acceleration or the deceleration. Note that,when the thickness change of the electrode plate 2 due to the change inthe line speed is different between the driving side and the operationside due to the difference in rigidity between the driving side and theoperation side of the roll press device 1, the differential pressureduring the acceleration period or the deceleration period may bechanged.

The correction value calculator 815 is supplied with the accelerationstart time, the acceleration end time, the line speed V₀ at the start ofacceleration, and the acceleration α from the line speed setting changer819, before the start of acceleration of the conveyance line. Forexample, when the roll press device 1 starts and when the line speedchanges during starting, these pieces of information are supplied fromthe line speed setting changer 819. In addition, the correction valuecalculator 815 is supplied with the deceleration start time, thedeceleration end time, the line speed V₀ at the start of deceleration,and the deceleration a from the line speed setting changer 819, beforethe start of deceleration of the conveyance line.

The correction value calculator 815 calculates a change amount ΔV_(s) ofthe line speed after S seconds from the start of the acceleration, onthe basis of the above (Formula 26), the line speed V₀ at the start ofthe acceleration, and the acceleration α. The correction valuecalculator 815 applies the calculated change amount ΔV_(s) of the linespeed to the above (Formula 27) to predict the change amount ΔT_(ave,s)of the thickness average value T_(ave) after S seconds from the start ofacceleration. The correction value calculator 815 calculates acorrection value ΔP_(ave,s) of the average press pressure P_(ave) forcausing the change amount ΔT_(ave,s) of the thickness average valueT_(ave) to be zero, on the basis of the above (Formula 31).

In the example illustrated in FIG. 10 , the correction value calculator815 calculates correction values ΔP_(0.1), ΔP_(0.2), . . . , andΔP_(tend) of the average press pressure P_(ave) at intervals of 0.1seconds, and supplies the calculated correction values ΔP_(0.1),ΔP_(0.2), . . . , and ΔP_(tend) of the average press pressure P_(ave) tothe setting value corrector 816.

The setting value corrector 816 is supplied with the correction valuesΔP_(0.1), ΔP_(0.2), . . . , and ΔP_(tend) of the average press pressureP_(ave) from the correction value calculator 815. The setting valuecorrector 816 adds the correction values ΔP_(0.1), ΔP_(0.2), . . . , andΔP_(tend) to the press pressure setting value P₀ at the start ofacceleration to calculate corrected press pressure setting valuesP₀+ΔP_(0.1), P₀+ΔP_(0.2), . . . , and P₀+ΔP_(tend). The press pressuresetting value P₀ at the start of acceleration is, for example, the presspressure setting value P input by the operator via the HMI. The settingvalue corrector 816 supplies the calculated corrected press pressuresetting values P₀+ΔP_(0.1), P₀+ΔP_(0.2), . . . , and P₀+ΔP_(tend) to thepress pressure deviation calculator 817 c.

The press pressure deviation calculator 817 c calculates, at each time,a deviation between the press pressure setting value of the correctedpress pressure setting values P₀+ΔP_(0.1), P₀+ΔP_(0.2), . . . , andP₀+ΔP_(tend) supplied from the setting value corrector 816 allocated tothe first press cylinder 41 a and the actually measured pressure valueof the first press cylinder 41 a. In addition, the press pressuredeviation calculator 817 c calculates, at each time, a deviation betweenthe press pressure setting value of the corrected press pressure settingvalues P₀+ΔP_(0.1), P₀+ΔP_(0.2), . . . , and P₀+ΔP_(tend) supplied fromthe setting value corrector 816 allocated to the second press cylinder42 a and the actually measured pressure value of the second presscylinder 42 a. Each of the actually measured pressure value of the firstpress cylinder 41 a and the actually measured pressure value of thesecond press cylinder 42 a can be estimated according to, for example, ameasurement value of a valve opening meter.

The press pressure deviation calculator 817 c supplies the calculatedpressure deviation of the first press cylinder 41 a and the calculatedpressure deviation of the second press cylinder 42 a to the PIDcontroller 817 b. The PID controller 817 b generates a pressureoperation amount of the first press cylinder 41 a and a pressureoperation amount of the second press cylinder 42 a, on the basis of thepressure deviation of the first press cylinder 41 a and the pressuredeviation of the second press cylinder 42 a.

The PID controller 817 b supplies the generated pressure operationamount of the first press cylinder 41 a and the generated pressureoperation amount of the second press cylinder 42 a to the press pressurecontroller 817 a. The press pressure controller 817 a includes anactuator and drives each of the first press cylinder 41 a and the secondpress cylinder 42 a on the basis of the pressure operation amount of thefirst press cylinder 41 a and the pressure operation amount of thesecond press cylinder 42 a. Although acceleration is assumed in theabove description, the same control is performed during deceleration.

It is necessary to consider a delay time (time lag t_(e)) from thechange of the press pressure setting value to the change of the actualpress pressure. Therefore, the line speed setting changer 819 supplies acommand value for the line speed change to the line speed controller8110 at timing delayed by a time corresponding to the time lag t_(e)from timing at which a command to change the setting value of the presspressure is given to the correction value calculator 815. As a result,the operation of the actuator can be more appropriately changed withrespect to the change in the line speed, and the thickness of theelectrode plate 2 can be corrected with high accuracy. As describedabove, it is desirable to use a highly responsive hydraulic servo valvefor pressure control of the first press cylinder 41 a and the secondpress cylinder 42 a.

As described above, in the feedforward control example 1, the thicknesschange of the electrode plate 2 due to the change in the line speed ispredicted, the press pressure necessary for maintaining the thickness ofthe electrode plate 2 constantly is calculated, and the press pressureis changed by feedforward control. As a result, the thickness change ofthe electrode plate 2 during the acceleration period or the decelerationperiod of the conveyance line can be suppressed with high accuracy.

FIG. 11 is a diagram illustrating a feedforward control example 2 usingthe first control panel 81. The feedforward control example 2 is controlused in the roll press device according to the second embodimentillustrated in FIG. 2 . In the feedforward control example 2, the firstpress cylinder 41 a and the second press cylinder 42 a are used as thecompression mechanism. Hereinafter, differences from the feedforwardcontrol example 1 illustrated in FIG. 10 will be described. In thefeedforward control example 2, instead of the press pressure controller817 a, the PID controller 817 b, and the press pressure deviationcalculator 817 c, a cylinder position controller 817 d, a PID controller817 e, and a cylinder position deviation calculator 817 f are provided.

In the feedforward control example 2, by causing the positions of thefirst electric screw 41 b and the second electric screw 42 b to beconstant and changing the pressures of the first press cylinder 41 a andthe second press cylinder 42 a, the press load acting on the electrodeplate 2 is changed. The cylinder position of the first press cylinder 41a is measured by the first magnescale 41 c, and the pressure of thefirst press cylinder 41 a is controlled such that the cylinder positionof the first press cylinder 41 a maintains the setting value. Similarly,the cylinder position of the second press cylinder 42 a is measured bythe second magnescale 42 c, and the pressure of the second presscylinder 42 a is controlled such that the cylinder position of thesecond press cylinder 42 a maintains the setting value. Since there is aproportional relation between the change amount ΔG_(ave) of the averagepress cylinder position G_(ave)=(G_(m)+G_(s))/2 of the driving-sidepress cylinder position G_(m) and the operation-side press cylinderposition G_(s) and the change amount ΔT_(ave) of the thickness averagevalue T_(ave) of the electrode plate 2, a relation of the following(Formula 32) holds between the change amount ΔG_(ave) of the averagepress cylinder position G_(ave) and the change amount ΔT_(ave) of thethickness average value T_(ave) when the cylinder position is changed.

ΔT _(ave) =G×ΔG _(ave)  (Formula 32)

G is a proportional constant.

The correction value ΔG_(ave,s) of the average press cylinder positionG_(ave) for causing the change amount ΔT_(ave,s) of the thicknessaverage value T_(ave) after S seconds from the start of acceleration ordeceleration to be zero can be obtained by the following (Formula 33)after removing ΔV_(s) and ΔT_(ave) from the relations of the above(Formula 26), (Formula 27), and (Formula 32).

ΔG _(ave,s)={(D×α)/G}×S  (Formula 33)

When the average press cylinder position at the time of acceleration ordeceleration is G_(ave,0), the cylinder positions of the first presscylinder 41 a and the second press cylinder 42 a arefeedforward-controlled such that the average press cylinder positionafter S seconds becomes G_(ave,0)+ΔG_(ave,s). As a result, a change inthe thickness of the electrode plate 2 due to a change in the line speedcan be suppressed.

The difference between the driving-side press cylinder position G_(m)and the operation-side press cylinder position G_(s) during theacceleration period or the deceleration period of the conveyance linemay be basically the same as that before the acceleration or thedeceleration. Note that, when the thickness change of the electrodeplate 2 due to the change in line speed is different between the drivingside and the operation side due to the difference in rigidity betweenthe driving side and the operation side of the roll press device 1, thedifference during the acceleration period or the deceleration period maybe changed.

The correction value calculator 815 is supplied with the accelerationstart time, the acceleration end time, the line speed V₀ at the start ofacceleration, and the acceleration α from the line speed setting changer819, before the start of acceleration of the conveyance line. Inaddition, the correction value calculator 815 is supplied with thedeceleration start time, the deceleration end time, the line speed V₀ atthe start of deceleration, and the deceleration a from the line speedsetting changer 819, before the start of deceleration of the conveyanceline.

The correction value calculator 815 calculates a change amount ΔV_(s) ofthe line speed after S seconds from the start of the acceleration, onthe basis of the above (Formula 26), the line speed V₀ at the start ofthe acceleration, and the acceleration α. The correction valuecalculator 815 applies the calculated change amount ΔV_(s) of the linespeed to the above (Formula 27) to predict the change amount ΔT_(ave,s)of the thickness average value T_(ave) after S seconds from the start ofacceleration. The correction value calculator 815 calculates acorrection value ΔG_(ave,s) of the average press cylinder positionG_(ave) for causing the change amount ΔT_(ave,s) of the thicknessaverage value T_(ave) to be zero, on the basis of the above (Formula33).

In the example illustrated in FIG. 11 , the correction value calculator815 calculates the correction values ΔG_(0.1), ΔG_(0.2), . . . , andΔG_(tend) of the average press cylinder position G_(ave) at intervals of0.1 seconds, and supplies the calculated correction values ΔG_(0.1),ΔG_(0.2), . . . , and ΔG_(tend) of the average press cylinder positionG_(ave) to the setting value corrector 816.

The setting value corrector 816 is supplied with the correction valuesΔG_(0.1), ΔG_(0.2), . . . , and ΔG_(tend) of the average press cylinderposition G_(ave) from the correction value calculator 815. The settingvalue corrector 816 adds the correction values ΔG_(0.1), ΔG_(0.2), . . ., and ΔG_(tend) to the press cylinder position setting value G₀ at thestart of acceleration to calculate corrected press cylinder positionsetting values G₀+ΔG_(0.1), G₀+ΔG₀₂, . . . , and G₀+ΔG_(tend). The presscylinder position setting value G₀ at the start of acceleration is, forexample, the press cylinder position setting value G input by theoperator via the HMI. The setting value corrector 816 supplies thecalculated corrected press cylinder position setting values G₀+ΔG_(0.1),G₀+ΔG_(0.2), . . . , and G₀+ΔG_(tend) to the cylinder position deviationcalculator 817 f.

The cylinder position deviation calculator 817 f calculates a deviationbetween the corrected press cylinder position setting valuesG₀+ΔG_(0.1), G₀+ΔG_(0.2), . . . , and G₀+ΔG_(tend) supplied from thesetting value corrector 816 and the actual measurement value of thecylinder position of the first press cylinder 41 a measured by the firstmagnescale 41 c at each time. In addition, the cylinder positiondeviation calculator 817 f calculates a deviation between the correctedpress cylinder position setting values G₀+ΔG_(0.1), G₀+ΔG_(0.2), . . . ,and G₀+ΔG_(tend) supplied from the setting value corrector 816 and theactual measurement value of the cylinder position of the second presscylinder 42 a measured by the second magnescale 42 c at each time.

The cylinder position deviation calculator 817 f supplies the calculatedcylinder position deviation of the first press cylinder 41 a and thecalculated cylinder position deviation of the second press cylinder 42 ato the PID controller 817 e. The PID controller 817 e generates thepressure operation amount of the first press cylinder 41 a and thepressure operation amount of the second press cylinder 42 a, on thebasis of the cylinder position deviation of the first press cylinder 41a and the cylinder position deviation of the second press cylinder 42 a.

The PID controller 817 e supplies the generated pressure operationamount of the first press cylinder 41 a and the generated pressureoperation amount of the second press cylinder 42 a to the cylinderposition controller 817 d. The cylinder position controller 817 dincludes an actuator and drives each of the first press cylinder 41 aand the second press cylinder 42 a on the basis of the pressureoperation amount of the first press cylinder 41 a and the pressureoperation amount of the second press cylinder 42 a. Althoughacceleration is assumed in the above description, the same control isperformed during deceleration.

It is necessary to consider a delay time (time lag t_(e)) from thechange of the cylinder position setting value to the change of theactual cylinder position. Therefore, the line speed setting changer 819supplies a command value for the line speed change to the line speedcontroller 8110 at timing delayed by a time corresponding to the timelag t_(e) from timing at which a command to change the setting value ofthe cylinder position is given to the correction value calculator 815.As a result, the operation of the actuator can be more appropriatelychanged with respect to the change in the line speed, and the thicknessof the electrode plate 2 can be corrected with high accuracy. Asdescribed above, it is desirable to use a highly responsive hydraulicservo valve for pressure control of the first press cylinder 41 a andthe second press cylinder 42 a.

As described above, in the feedforward control example 2, the thicknesschange of the electrode plate 2 due to the change in the line speed ispredicted, the press cylinder position necessary for maintaining thethickness of the electrode plate 2 constantly is calculated, and thepress cylinder position is changed by feedforward control. As a result,the thickness change of the electrode plate 2 during the accelerationperiod or the deceleration period of the conveyance line can besuppressed with high accuracy.

FIG. 12 is a diagram illustrating a feedforward control example 3 usingthe first control panel 81. The feedforward control example 3 is controlused in the roll press device according to the first embodimentillustrated in FIG. 1 . In the feedforward control example 3, the firstelectric screw 41 b and the second electric screw 42 b are used as thecompression mechanism. Hereinafter, differences from the feedforwardcontrol example 1 illustrated in FIG. 10 will be described. In thefeedforward control example 3, instead of the press pressure controller817 a, the PID controller 817 b, and the press pressure deviationcalculator 817 c, a screw position controller 817 g, a PID controller817 h, and a screw position deviation calculator 817 i are provided.

In the feedforward control example 3, a sufficiently large pressure(fixed value) is applied to the first press cylinder 41 a and the secondpress cylinder 42 a to prevent the cylinder position from changing dueto the position change of the first electric screw 41 b and the secondelectric screw 42 b. In this state, the press load acting on theelectrode plate 2 is changed by changing the positions of the firstelectric screw 41 b and the second electric screw 42 b. The positions ofthe first electric screw 41 b and the second electric screw 42 b arecontrolled by the servomotor. Since there is a proportional relationbetween the change amount ΔD_(ave) of the average electric screwposition D_(ave)=(D_(m)+D_(s))/2 of the driving-side electric screwposition D_(m) and the operation-side electric screw position D_(s) andthe change amount ΔT_(ave) of the thickness average value T_(ave) of theelectrode plate 2, a relation of the following (Formula 34) holdsbetween the change amount ΔD_(ave) of the average electric screwposition D_(ave) and the change amount ΔT_(ave) of the thickness averagevalue T_(ave) when the electric screw position is changed.

ΔT _(ave) =H×ΔD _(ave)  (Formula 34)

H is a proportional constant.

The correction value ΔD_(ave,s) of the average electric screw positionD_(ave) for causing the change amount ΔT_(ave,s) of the thicknessaverage value T_(ave) after S seconds from the start of acceleration ordeceleration to be zero can be obtained by the following (Formula 35)after removing ΔV_(s) and ΔT_(ave) from the relations of the above(Formula 26), (Formula 27), and (Formula 34).

ΔD _(ave,s)={(D×a)/H}×S  (Formula 35)

When the average electric screw position at the time of acceleration ordeceleration is set to D_(ave,0), the positions of the first electricscrew 41 b and the second electric screw 42 b are feedforward-controlledsuch that the average electric screw position after S seconds becomesD_(ave,0)+ΔD_(ave,s). As a result, a change in the thickness of theelectrode plate 2 due to a change in the line speed can be suppressed.

The difference between the driving-side electric screw position D_(m)and the operation-side electric screw position D_(s) in the accelerationperiod or the deceleration period of the conveyance line may bebasically the same as that before the acceleration or the deceleration.Note that, when the thickness change of the electrode plate 2 due to thechange in line speed is different between the driving side and theoperation side due to the difference in rigidity between the drivingside and the operation side of the roll press device 1, the differenceduring the acceleration period or the deceleration period may bechanged.

The correction value calculator 815 is supplied with the accelerationstart time, the acceleration end time, the line speed V₀ at the start ofacceleration, and the acceleration α from the line speed setting changer819, before the start of acceleration of the conveyance line. Inaddition, the correction value calculator 815 is supplied with thedeceleration start time, the deceleration end time, the line speed V₀ atthe start of deceleration, and the deceleration a from the line speedsetting changer 819, before the start of deceleration of the conveyanceline.

The correction value calculator 815 calculates a change amount ΔV_(s) ofthe line speed after S seconds from the start of the acceleration, onthe basis of the above (Formula 26), the line speed V₀ at the start ofthe acceleration, and the acceleration α. The correction valuecalculator 815 applies the calculated change amount ΔV_(s) of the linespeed to the above (Formula 27) to predict the change amount ΔT_(ave,s)of the thickness average value T_(ave) after S seconds from the start ofacceleration. The correction value calculator 815 calculates acorrection value ΔD_(ave,s) of the average electric screw positionD_(ave) for causing the change amount ΔT_(ave,s) of the thicknessaverage value T_(ave) to be zero, on the basis of the above (Formula35).

In the example illustrated in FIG. 12 , the correction value calculator815 calculates the correction values ΔD_(0.1), ΔD_(0.2), . . . , andΔD_(tend) of the average electric screw position D_(ave) at intervals of0.1 seconds, and supplies the calculated correction values ΔD_(0.1),ΔD_(0.2), . . . , and ΔD_(tend) of the average electric screw positionD_(ave) to the setting value corrector 816.

The setting value corrector 816 is supplied with the correction valuesΔD_(0.1), ΔD_(0.2), . . . , and ΔD_(tend) of the average electric screwposition D_(ave) from the correction value calculator 815. The settingvalue corrector 816 adds the correction values ΔD_(0.1), ΔD_(0.2), . . ., and ΔD_(tend) to the electric screw position setting value D₀ at thestart of acceleration to calculate corrected electric screw positionsetting values D₀+ΔD_(0.1), D₀+ΔD_(0.2), . . . , and D₀+ΔD_(tend). Theelectric screw position setting value D₀ at the start of accelerationis, for example, the electric screw position setting value D input bythe operator via the HMI. The setting value corrector 816 supplies thecalculated corrected electric screw position setting values D₀+ΔD_(0.1),D₀+ΔD_(0.2), . . . , and D₀+ΔD_(tend) to the screw position deviationcalculator 817 i.

The screw position deviation calculator 817 i calculates a deviationbetween the corrected electric screw position setting valuesD₀+ΔD_(0.1), D₀+ΔD_(0.2), . . . , and D₀+ΔD_(tend) supplied from thesetting value corrector 816 and the measurement value of the position ofthe first electric screw 41 b at each time. In addition, the screwposition deviation calculator 817 i calculates a deviation between thecorrected electric screw position setting values D₀+ΔD_(0.1),D₀+ΔD_(0.2), . . . , and D₀+ΔD_(tend) supplied from the setting valuecorrector 816 and the measurement value of the position of the secondelectric screw 42 b at each time.

The screw position controller 817 g includes servo motors for reducingthe pressures of the first electric screw 41 b and the second electricscrew 42 b, respectively. A position change amount of each of the firstelectric screw 41 b and the second electric screw 42 b can be calculatedfrom the rotation speed of each servomotor.

The screw position deviation calculator 817 i supplies the calculatedposition deviation of the first electric screw 41 b and the calculatedposition deviation of the second electric screw 42 b to the PIDcontroller 817 h. The PID controller 817 h generates a rotationoperation amount of the servomotor for the first electric screw 41 b anda rotation operation amount of the servomotor for the second electricscrew 42 b, on the basis of the position deviation of the first electricscrew 41 b and the position deviation of the second electric screw 42 b.

The PID controller 817 h supplies the generated rotation operationamount of the servomotor for the first electric screw 41 b and thegenerated rotation operation amount of the servomotor for the secondelectric screw 42 b to the screw position controller 817 g. The screwposition controller 817 g drives each of the servomotor for the firstelectric screw 41 b and the servomotor for the second electric screw 42b, on the basis of the rotation operation amount of the servomotor forthe first electric screw 41 b and the rotation operation amount of theservomotor for the second electric screw 42 b. Although acceleration isassumed in the above description, the same control is performed duringdeceleration.

It is necessary to consider a delay time (time lag t_(e)) from thechange of the electric screw position setting value to the change of theactual electric screw position. Therefore, the line speed settingchanger 819 supplies a command value for the line speed change to theline speed controller 8110 at timing delayed by a time corresponding tothe time lag t_(e) from timing at which a command to change the settingvalue of the electric crew position is given to the correction valuecalculator 815. As a result, the operation of the servo motor can bemore appropriately changed with respect to the change in the line speed,and the thickness of the electrode plate 2 can be corrected with highaccuracy.

As described above, in the feedforward control example 3, the thicknesschange of the electrode plate 2 due to the change in the line speed ispredicted, the electric screw position necessary for maintaining thethickness of the electrode plate 2 constantly is calculated, and theelectric screw position is changed by feedforward control. As a result,the thickness change of the electrode plate 2 during the accelerationperiod or the deceleration period of the conveyance line can besuppressed with high accuracy.

As described above, according to the feedback control examples 1 to 4using the roll press devices 1 according to the first to thirdembodiments, the first feature amount T_(t−m), the second feature amountT_(t−s), and the third feature amount T_(drop) are calculated on thebasis of the driving-side thickness measurement value T_(m), the centerthickness measurement value T_(c), the operation-side thicknessmeasurement value T_(s), and the thickness target value T_(t), and thecompression mechanism and/or the bend mechanism is controlled such thatall of the first feature amount T_(t−m), the second feature amountT_(t−s), and the third feature amount T_(drop) become zero. As thecompression mechanism, the press mechanism or the cotter mechanism canbe used. As a result, the thickness of the electrode plate 2 after thecompression processing can converged to the target value T_(t) over theentire width.

The above Patent Literature 1 (JP 2013-111647 A) discloses a method formeasuring the thicknesses after compression at the three positions ofthe operation side, the center portion, and the driving side, andcontrolling the press mechanism and the bend mechanism such that adifference between the measured thickness value and the target thicknessfalls within the preset threshold when the difference falls outside thethreshold. In this method, since the film thickness control is notactivated until the film thickness exceeds the threshold, thicknessaccuracy of the threshold or more cannot be obtained, and it may taketime to converge to the vicinity of the target thickness or it may notbe possible to converge to the vicinity of the target thickness.

In the above method, the driving-side thickness, the operation-sidethickness, and the target thickness are compared, and when at least oneof the driving-side thickness or the operation-side thickness exceedsthe threshold, the position of the press cylinder is reset so as tocorrect the thickness, and the pressure of the bend cylinder iscalculated and set to maintain the deflection correction amount thatchanges due to the position change of the press cylinder. When both thedriving-side thickness and the operation-side thickness do not exceedthe threshold, the center portion thickness is compared with thethreshold. When the center portion thickness exceeds the threshold, itis determined that the roll deformation of the center portion is large,and only the pressure of the bend cylinder is changed and the positionof the press cylinder is not changed. This control flow is repeatedlyexecuted.

In general, the pressure change of the bend cylinder acts in a directionof opening the roll gap, and changes the rolling load on the material tobe rolled, so that the thickness change is involved. Therefore, even inany procedure in the control flow, the film thickness is changed bychanging the pressure of the bend cylinder, and the film thicknessdeviates again from the threshold, so that it takes time to reach thevicinity of the target thickness, or the film thickness cannot becontrolled to the threshold in some cases. In particular, when thethreshold decreases or when the position of the press cylinder or thepressure of the bend cylinder needs to be greatly changed, thepossibility that the film thickness deviates again from the thresholdincreases, so that there is a limit to the thickness range or thecontrol speed that can be controlled.

As described above, the driving-side thickness, the operation-sidethickness, and the target thickness are compared, and when both thedriving-side thickness and the operation-side thickness do not exceedthe threshold, the center portion thickness and the threshold arecompared. When the center portion thickness exceeds the threshold, it isdetermined that the roll deflection is large, and only the pressure ofthe bend cylinder is changed. In this case, since the center thicknessis controlled after the thicknesses of both ends are controlled to thethreshold or less, it takes time to converge to the target thickness.Furthermore, in the course of controlling the thicknesses of both ends,the center thickness may deviate from the target thickness. For example,when the center thickness is larger than the target thickness and thethicknesses of both ends are smaller than the target thickness, theloads of both sides are controlled to be lowered such that thethicknesses of both ends become the target thickness. However, since thepressure from the press roll acting on the center portion of theelectrode plate also decreases, the center thickness increases anddeviates from the target value.

On the other hand, according to the feedback control examples 1 to 4using the roll press devices 1 according to the first to thirdembodiments, the magnitude of the roll deflection and the direction ofthe roll deflection are determined by the difference (third featureamount T_(drop)) between the center thickness and the average of theboth end thicknesses, and the difference between the center thicknessand the both end thicknesses due to the roll deflection issimultaneously controlled while the both end thicknesses are controlled.As a result, it is possible to more quickly converge the thickness ofthe electrode plate 2 to the target value over the entire width withoutdeteriorating the thickness in the width direction.

As described above, according to the feedback control examples 1 to 4using the roll press devices 1 according to the first to thirdembodiments, the feedback control is performed such that the thicknessof the electrode plate 2 after the compression processing alwaysconverges to the target value T_(t). As a result, the thickness of theelectrode plate 2 is always maintained in a favorable state. Inaddition, since the thickness of the electrode plate 2 is automaticallycontrolled to the target value T_(t), it is not necessary for theoperator to stop the line periodically, measure the thickness of theelectrode plate 2 with a micrometer, and adjust the pressure value ofthe compression mechanism and/or the bend mechanism on the basis of themeasurement value. Therefore, it is not necessary to deploy a skilledoperator, and labor costs can be suppressed. Further, it is possible tosuppress variations in quality caused by the operator.

In addition, according to the feedback control examples 1 to 4 using theroll press devices 1 according to the first to third embodiments, inorder to prevent execution of correction of a new setting value on thebasis of the thickness measurement value before the correction of thesetting value is reflected, the time t_(d) required to reach a statewhere the length of the electrode plate 2 reaches the pass line lengthL_(t) from the press position to the thickness meter 70 and thecorrection of the setting value is reflected in the thicknessmeasurement value after execution of the correction of the setting valueelapses and then the thickness measurement value is acquired. The threefeature amounts are calculated on the basis of the acquired thicknessmeasurement value, the correction value is calculated on the basis ofthe three feature amounts, and the next setting value change isexecuted.

In the coating step or the drying step in the pre-pressing step, thethickness of the material to be rolled after pressing may change due toa change in the thickness of the coating film of the material to berolled, a change in the hardness of the coating film, or a thermalinfluence of the pressure roller or the main bearing. Even in this case,by repeatedly and continuously performing the above control, immediatelyafter the thickness meter 70 detects the thickness change, the thicknessof the material to be rolled after pressing can be controlled to thetarget value T_(t) in the entire width, so that the good thickness canbe obtained over the entire length.

Further, by using the feedforward control examples 1 to 3 incombination, the thickness change of the electrode plate 2 at the timeof acceleration or deceleration of the conveyance line can be suppressedwith high accuracy. That is, by predicting the thickness change of theelectrode plate 2 due to the change in the line speed, calculating thecompression condition for causing the predicted thickness change to bezero, and feedforward-controlling the compression mechanism, thethickness change due to the change in the line speed can be suppressedwith high accuracy.

Since each proportional constant described above varies depending on theproduct type of the material to be rolled, it is desirable to measurethe proportional constant for each product type.

The present disclosure has been described on the basis of theembodiments. The embodiments are merely examples, and it is understoodby those skilled in the art that various modifications can be made inthe combination of the respective components or the respectiveprocessing processes, and that the modifications are also within thescope of the present disclosure.

In FIG. 3 , an example has been described in which the control device 80includes the two control panels of the first control panel 81 and thesecond control panel 82. However, the control device 80 may include onecontrol panel in which the first control panel 81 and the second controlpanel 82 are integrated.

In addition, in the above-described first to third embodiments, anexample has been described in which the compression mechanism and/or thebend mechanism is controlled such that all of the first feature amountT_(t−m), the second feature amount T_(t−s), and the third feature amountT_(drop) become zero. A state in which the third feature amount T_(drop)is zero and the difference between the driving-side thicknessmeasurement value T_(m) and the operation-side thickness measurementvalue T_(s) is also zero is a state in which the electrode plate 2 isflat in the width direction. In this regard, in the case ofmanufacturing the electrode plate 2 in which both edges are thicker thanthe center, the compression mechanism and/or the bend mechanism iscontrolled such that the third feature amount T_(drop) has a negativevalue corresponding to the thickness difference between the edge and thecenter. In the case of manufacturing the electrode plate 2 in which bothedges are thinner than the center, the compression mechanism and/or thebend mechanism is controlled such that the third feature amount T_(drop)has a positive value corresponding to the thickness difference betweenthe edge and the center.

That is, the electrode plate 2 having an arbitrary thickness profile canbe manufactured by arbitrarily setting β, γ, and δ in the following(Formula 35) to (Formula 37).

T _(t−m)+β=0  (Formula 35)

T _(t−s)+γ=0  (Formula 36)

T _(drop)+δ=0  (Formula 37)

β, γ, and δ are arbitrary real numbers [μm].

In the first to third embodiments described above, the third featureamount indicating the secondary component of the thickness profile ofthe electrode plate is defined by the difference between the centerthickness measurement value T_(c) and the average value of thedriving-side thickness measurement value T_(m) and the operation-sidethickness measurement value T_(s). In this regard, the third featureamount can also be defined from a quadratic or quaternary approximatecurve derived using the least squares method on the basis of thethickness measurement values at three or more points. When the quadraticcurve is approximated, the feature amount calculator 814 sets aquadratic coefficient of the approximated quadratic curve to the thirdfeature amount. When the quaternary curve is approximated, the featureamount calculator 814 sets a quadratic coefficient of the approximatedquaternary curve to the third feature amount. In general, when thenumber of sample points increases, the approximation accuracy isimproved. In addition, a quadratic coefficient can be derived if thefunction is a quadratic or higher function.

When thickness measurement values at five or more points are acquired,the first feature amount T_(t−m) is defined by a deviation between thethickness target value T_(t) and the thickness measurement value T_(m)at the most driving-side point among the five or more points, and thesecond feature amount T_(t−s) is defined by a deviation between thethickness target value T_(t) and the thickness measurement value T_(s)at the most operation-side point among the five or more points.

Note that the embodiments may be specified by the following items.

[Item 1]

A roll press device (1) comprising:

a first pressure roller (11) and a second pressure roller (12)structured to roll an electrode plate (2) of a secondary battery to becontinuously conveyed by sandwiching the electrode plate (2);

a first main bearing (21) and a second main bearing (22) provided on oneside and the other side of a rotation shaft of the first pressure roller(11), respectively, and structured to rotatably support the rotationshaft;

a third main bearing (23) and a fourth main bearing (24) provided on oneside and the other side of a rotation shaft of the second pressureroller (12), respectively, and structured to rotatably support therotation shaft;

a first bend bearing (31) and a second bend bearing (32) provided on oneside and the other side of the rotation shaft of the first pressureroller (11), respectively, and structured to rotatably support therotation shaft;

a third bend bearing (33) and a fourth main bearing (24) provided on oneside and the other side of the rotation shaft of the second pressureroller (12), respectively, and structured to rotatably support therotation shaft;

a first compression mechanism (41) capable of applying a load to atleast one of the first main bearing (21) and the third main bearing (23)in a direction in which the first pressure roller (11) and the secondpressure roller (12) approach each other;

a second compression mechanism (42) capable of applying a load to atleast one of the second main bearing (22) and the fourth bend bearing(34) in a direction in which the first pressure roller (11) and thesecond pressure roller (12) approach each other;

a first bend mechanism (51) capable of applying a load to at least oneof the first bend bearing (31) and the third bend bearing (33) in adirection in which the first pressure roller (11) and the secondpressure roller (12) are separated from each other;

a second bend mechanism (52) capable of applying a load to at least oneof the second bend bearing (32) and the fourth bend bearing (34) in adirection in which the first pressure roller (11) and the secondpressure roller (12) are separated from each other;

a thickness meter (70) provided on the exit side of the first pressureroller (11) and the second pressure roller (12) and structured to detecta thickness of the electrode plate (2) of the secondary battery at threeor more points in a width direction of the electrode plate (2);

a calculator (814 to 816) structured to calculate setting values of thefirst compression mechanism (41), the second compression mechanism (42),the first bend mechanism (51), and the second bend mechanism (52) on thebasis of thickness measurement values at the three or more points basedon detection values of the thickness meter (70) and a thickness targetvalue; and

a controller (817, 818) structured to control loads of the firstcompression mechanism (41), the second compression mechanism (42), thefirst bend mechanism (51), and the second bend mechanism (52) on thebasis of the setting values calculated by the calculator (814 to 816),

wherein the calculator (814 to 816) calculates three feature amounts ofa first deviation between the thickness target value and a thicknessmeasurement value of a point closest to the first compression mechanism(41) among the three or more points, a second deviation between thethickness target value and a thickness measurement value of a pointclosest to the second compression mechanism (42) among the three or morepoints, and a secondary component of a thickness profile of theelectrode plate (2), and adaptively changes the setting values of thefirst compression mechanism (41), the second compression mechanism (42),the first bend mechanism (51), and the second bend mechanism (52) on thebasis of the three feature amounts.

According to this, it is possible to realize high accuracy of thicknesscontrol of the electrode plate (2) by the roll press device (1).

[Item 2]

The roll press device (1) according to item 1, wherein

the thickness meter (70) is provided on the exit side of the firstpressure roller (11) and the second pressure roller (12), and detectsthe thickness of the electrode plate (2) of the secondary battery ateach of a first point, a second point, and a third point arranged in thewidth direction of the electrode plate (2),

the calculator (814 to 816) calculates setting values of the firstcompression mechanism (41), the second compression mechanism (42), thefirst bend mechanism (51), and the second bend mechanism (52) on thebasis of a first point thickness measurement value, a second pointthickness measurement value, and a third point thickness measurementvalue based on detection values of the thickness meter (70) and thethickness target value,

the first point is set to an end portion of the electrode plate (2) ofthe secondary battery on the side where the first compression mechanism(41) is provided,

the second point is set to a center portion of the electrode plate (2)of the secondary battery,

the third point is set to an end portion of the electrode plate (2) ofthe secondary battery on the side where the second compression mechanism(42) is provided,

the calculator (814 to 816) calculates three feature amounts of a firstdeviation between the first point thickness measurement value and thethickness target value, a second deviation between the third pointthickness measurement value and the thickness target value, and asecondary component of a thickness profile of the electrode plate (2)from the first point thickness measurement value, the second pointthickness measurement value, the third point thickness measurementvalue, and the thickness target value, and

the secondary component of the thickness profile of the electrode plate(2) is defined by a difference between the second point thicknessmeasurement value and an average value of the first point thicknessmeasurement value and the third point thickness measurement value.

According to this, the thickness of the electrode plate (2) in the widthdirection can be profiled with high accuracy by the three featureamounts calculated from the thickness measurement values at the threepoints.

[Item 3]

The roll press device (1) according to item 1 or 2, wherein

the calculator (814 to 816) calculates setting values of the firstcompression mechanism (41), the second compression mechanism (42), thefirst bend mechanism (51), and the second bend mechanism (52) such thatall of the three feature amounts become zero, on the basis of a relationbetween a load generated by the first compression mechanism (41), thesecond compression mechanism (42), the first bend mechanism (51), andthe second bend mechanism (52) and the three feature amounts, which isderived in advance.

According to this, the thickness change of the electrode plate (2) canbe suppressed with high accuracy by feedback control using the threefeature amounts.

[Item 4]

The roll press device (1) according to item 3, wherein

the first compression mechanism (41) includes a first press cylinder (41a),

the second compression mechanism (42) includes a second press cylinder(42 a),

the first bend mechanism (51) includes a first bend cylinder (51 a or 51b, 51 c),

the second bend mechanism (52) includes a second bend cylinder (52 a or52 b, 52 c), and

the calculator (814 to 816) calculates setting values of a pressure ofthe first press cylinder (41 a), a pressure of the second press cylinder(42 a), a pressure of the first bend cylinder (51 a or 51 b, 51 c), anda pressure of the second bend cylinder (52 a or 52 b, 52 c) such thatall of the three feature amounts become zero.

According to this, by feedback-controlling the setting values of thepressure of the first press cylinder (41 a), the pressure of the secondpress cylinder (42 a), the pressure of the first bend cylinder (51 a or51 b, 51 c), and the pressure of the second bend cylinder (52 a or 52 b,52 c) using the three feature amounts, the thickness change of theelectrode plate (2) can be suppressed with high accuracy.

[Item 5]

The roll press device (1) according to item 3, wherein

the first compression mechanism (41) includes a first press cylinder (41a),

the second compression mechanism (42) includes a second press cylinder(42 a),

the first bend mechanism (51) includes a first bend cylinder (51 a or 51b, 51 c),

the second bend mechanism (52) includes a second bend cylinder (52 a or52 b, 52 c), and

the calculator (814 to 816) calculates setting values of a position ofthe first press cylinder (41 a), a position of the second press cylinder(42 a), a pressure of the first bend cylinder (51 a or 51 b, 51 c), anda pressure of the second bend cylinder (52 a or 52 b, 52 c) such thatall of the three feature amounts become zero.

According to this, by feedback-controlling the setting values of theposition of the first press cylinder (41 a), the position of the secondpress cylinder (42 a), the pressure of the first bend cylinder (51 a or51 b, 51 c), and the pressure of the second bend cylinder (52 a or 52 b,52 c) using the three feature amounts, the thickness change of theelectrode plate (2) can be suppressed with high accuracy.

[Item 6]

The roll press device (1) according to item 5, wherein

the first compression mechanism (41) further includes a first magnescale(41 c) to measure a position of the first press cylinder (41 a),

the second compression mechanism (42) further includes a secondmagnescale (42 c) to measure a position of the second press cylinder (42a), and

the controller (817 d, 818)

controls the pressure of the first press cylinder (41 a) such that theposition of the first press cylinder (41 a) measured by the firstmagnescale (41 c) and the position of the first press cylinder (41 a)supplied from the calculator (814 to 816) are matched with each other,and

controls the pressure of the second press cylinder (42 a) such that theposition of the second press cylinder (42 a) measured by the secondmagnescale (42 c) and the position of the second press cylinder (42 a)supplied from the calculator (814 to 816) are matched with each other.

According to this, the position of the first press cylinder (41 a) andthe position of the second press cylinder (42 a) can be measured withhigh accuracy using the first magnescale (41 c) and the secondmagnescale (42 c), and feedback control of the compression mechanismwith high responsiveness can be realized.

[Item 7]

The roll press device (1) according to item 3, wherein

the first compression mechanism (41) includes a first electric screw (41b),

the second compression mechanism (42) includes a second electric screw(42 b),

the first bend mechanism (51) includes a first bend cylinder (51 a or 51b, 51 c),

the second bend mechanism (52) includes a second bend cylinder (52 a or52 b, 52 c), and

the calculator (814 to 816) calculates setting values of a position ofthe first electric screw (41 b), a position of the second electric screw(42 b), a pressure of the first bend cylinder (51 a or 51 b, 51 c), anda pressure of the second bend cylinder (52 a or 52 b, 52 c) such thatall of the three feature amounts become zero.

According to this, by feedback-controlling the setting values of theposition of the first electric screw (41 b), the position of the secondelectric screw (42 b), the pressure of the first bend cylinder (51 a or51 b, 51 c), and the pressure of the second bend cylinder (52 a or 52 b,52 c) using the three feature amounts, the thickness change of theelectrode plate (2) can be suppressed with high accuracy.

[Item 8]

The roll press device (1) according to item 3, wherein

the first compression mechanism (41) includes a first electric cotter(41 e),

the second compression mechanism (42) includes a second electric cotter(42 e),

the first bend mechanism (51) includes a first bend cylinder (51 a or 51b, 51 c),

the second bend mechanism (52) includes a second bend cylinder (52 a or52 b, 52 c), and

the calculator (814 to 816) calculates setting values of a height of thefirst electric cotter (41 e), a height of the second electric cotter (42e), a pressure of the first bend cylinder (51 a or 51 b, 51 c), and apressure of the second bend cylinder (52 a or 52 b, 52 c) such that allof the three feature amounts become zero.

According to this, by feedback-controlling the height of the firstelectric cotter (41 e), the height of the second electric cotter (42 e),the pressure of the first bend cylinder (51 a or 51 b, 51 c), and thepressure of the second bend cylinder (52 a or 52 b, 52 c) using thethree feature amounts, the thickness change of the electrode plate (2)can be suppressed with high accuracy.

[Item 9]

The roll press device (1) according to any one of items 1 to 8, wherein

the thickness meter (70) continuously detects a thickness of theelectrode plate (2) by scanning one thickness detection sensor in awidth direction of the electrode plate (2), and extracts thicknessdetection values at the three or more points.

According to this, the number of thickness detection sensors can bereduced.

[Item 10]

The roll press device (1) according to any one of items 1 to 8, wherein

the thickness meter (70) detects thicknesses at the three or more pointswith three or more thickness detection sensors.

According to this, the control of each thickness detection sensor can besimplified.

[Item 11]

The roll press device (1) according to item 9 or 10, further comprising:

a thickness measurement value calculator (821) structured to calculatethickness measurement values at the three or more points by filteringthe three or more thickness detection values detected by the thicknessmeter (70) in a longitudinal direction of the electrode plate (2).

According to this, the noise of the detection value can be removed.

[Item 12]

The roll press device (1) according to any one of items 1 to 8, wherein

the calculator (814 to 816) suspends a next change of the setting valuesof the first compression mechanism (41), the second compressionmechanism (42), the first bend mechanism (51), and the second bendmechanism (52) until predetermined conditions regarding a pass linelength from a press position to the thickness meter (70) and areflection time of the changing of the setting values in an actualoutput after changing the setting values of the first compressionmechanism (41), the second compression mechanism (42), the first bendmechanism (51), and the second bend mechanism (52) are satisfied.

According to this, useless or excessive changes of the setting value ofthe compression mechanism and/or the bend mechanism can be avoided.

[Item 13]

A control device (80) used in a roll press device (1), which includes

a first pressure roller (11) and a second pressure roller (12) rollingan electrode plate (2) of a secondary battery to be continuouslyconveyed by sandwiching the electrode plate (2);

a first main bearing (21) and a second main bearing (22) provided on oneside and the other side of a rotation shaft of the first pressure roller(11), respectively, and rotatably supporting the rotation shaft;

a third main bearing (23) and a fourth main bearing (24) provided on oneside and the other side of a rotation shaft of the second pressureroller (12), respectively, and rotatably supporting the rotation shaft;a first bend bearing (31) and a second bend bearing (32) provided on oneside and the other side of the rotation shaft of the first pressureroller (11), respectively, and rotatably supporting the rotation shaft;

a third bend bearing (33) and a fourth main bearing (24) provided on oneside and the other side of the rotation shaft of the second pressureroller (12), respectively, and rotatably supporting the rotation shaft;

a first compression mechanism (41) capable of applying a load to atleast one of the first main bearing (21) and the third main bearing (23)in a direction in which the first pressure roller (11) and the secondpressure roller (12) approach each other;

a second compression mechanism (42) capable of applying a load to atleast one of the second main bearing (22) and the fourth bend bearing(34) in a direction in which the first pressure roller (11) and thesecond pressure roller (12) approach each other;

a first bend mechanism (51) capable of applying a load to at least oneof the first bend bearing (31) and the third bend bearing (33) in adirection in which the first pressure roller (11) and the secondpressure roller (12) are separated from each other;

a second bend mechanism (52) capable of applying a load to at least oneof the second bend bearing (32) and the fourth bend bearing (34) in adirection in which the first pressure roller (11) and the secondpressure roller (12) are separated from each other; and

a thickness meter (70) provided on the exit side of the first pressureroller (11) and the second pressure roller (12) and detecting athickness of the electrode plate (2) of the secondary battery at threeor more points in a width direction of the electrode plate (2),

the control device (80) comprising:

a calculator (814 to 816) structured to calculate setting values of thefirst compression mechanism (41), the second compression mechanism (42),the first bend mechanism (51), and the second bend mechanism (52) on thebasis of thickness measurement values at the three or more points basedon detection values of the thickness meter (70) and a thickness targetvalue; and

a controller (817, 818) structured to control loads of the firstcompression mechanism (41), the second compression mechanism (42), thefirst bend mechanism (51), and the second bend mechanism (52) on thebasis of the setting values calculated by the calculator (814 to 816),

wherein the calculator (814 to 816) calculates three feature amounts ofa first deviation between the thickness target value and a thicknessmeasurement value of a point closest to the first compression mechanism(41) among the three or more points, a second deviation between thethickness target value and a thickness measurement value of a pointclosest to the second compression mechanism (42) among the three or morepoints, and a secondary component of a thickness profile of theelectrode plate (2), and adaptively changes the setting values of thefirst compression mechanism (41), the second compression mechanism (42),the first bend mechanism (51), and the second bend mechanism (52) on thebasis of the three feature amounts.

According to this, it is possible to realize high accuracy of thicknesscontrol of the electrode plate (2) by the roll press device (1).

REFERENCE SIGNS LIST

-   -   1 roll press device, 2 electrode plate, 11 first pressure        roller, 12 second pressure roller, 13 unwinder, 14 winder, 15        motor, 16 pulse generator, 21 to 24 main bearing, 31 to 34 bend        bearing, 41 first compression mechanism, 42 second compression        mechanism, 41 a first press cylinder, 41 b first electric screw,        41 c first magnescale, 41 d first load cell, 41 e first electric        cotter, 42 a second press cylinder, 42 b second electric screw,        42 c second magnescale, 42 d second load cell, 42 e second        electric cotter, 51 first bend mechanism, 51 a first bend        cylinder, 51 b third bend cylinder, 51 c fifth bend cylinder, 52        a second bend cylinder, 52 b fourth bend cylinder, 52 c sixth        bend cylinder, 52 second bend mechanism, 61 first preload        mechanism, 61 a first preload cylinder, 62 second preload        mechanism, 62 a second preload cylinder, 70 thickness meter, 80        control device, 81 first control panel, 811 length measurer, 812        acquisition timing generator, 813 thickness measurement value        acquirer, 814 feature amount calculator, 815 correction value        calculator, 816 setting value corrector, 817 a press pressure        controller, 817 b PID controller, 817 c press pressure deviation        calculator, 817 d cylinder position controller, 817 e PID        controller, 817 f cylinder position deviation calculator, 817 g        screw position controller, 817 h PID controller, 817 i screw        position deviation calculator, 817 j cotter height controller,        817 k PID controller, 8171 cotter height deviation calculator,        818 a bend pressure controller, 818 b PID controller, 818 c bend        pressure deviation calculator, 819 line speed setting changer,        8110 line speed controller

1. A roll press device comprising: a first pressure roller and a secondpressure roller structured to roll an electrode plate of a secondarybattery to be continuously conveyed by sandwiching the electrode plate;a first main bearing and a second main bearing provided on one side andthe other side of a rotation shaft of the first pressure roller,respectively, and structured to rotatably support the rotation shaft; athird main bearing and a fourth main bearing provided on one side andthe other side of a rotation shaft of the second pressure roller,respectively, and structured to rotatably support the rotation shaft; afirst bend bearing and a second bend bearing provided on one side andthe other side of the rotation shaft of the first pressure roller,respectively, and structured to rotatably support the rotation shaft; athird bend bearing and a fourth bend bearing provided on one side andthe other side of the rotation shaft of the second pressure roller,respectively, and structured to rotatably support the rotation shaft; afirst compression mechanism capable of applying a load to at least oneof the first main bearing and the third main bearing in a direction inwhich the first pressure roller and the second pressure roller approacheach other; a second compression mechanism capable of applying a load toat least one of the second main bearing and the fourth main bearing in adirection in which the first pressure roller and the second pressureroller approach each other; a first bend mechanism capable of applying aload to at least one of the first bend bearing and the third bendbearing in a direction in which the first pressure roller and the secondpressure roller are separated from each other; a second bend mechanismcapable of applying a load to at least one of the second bend bearingand the fourth bend bearing in a direction in which the first pressureroller and the second pressure roller are separated from each other; athickness meter provided on the exit side of the first pressure rollerand the second pressure roller and structured to detect a thickness ofthe electrode plate of the secondary battery at three or more points ina width direction of the electrode plate; a calculator structured tocalculate setting values of the first compression mechanism, the secondcompression mechanism, the first bend mechanism, and the second bendmechanism on the basis of thickness measurement values at the three ormore points based on detection values of the thickness meter and athickness target value; and a controller structured to control loads ofthe first compression mechanism, the second compression mechanism, thefirst bend mechanism, and the second bend mechanism on the basis of thesetting values calculated by the calculator, wherein the calculatorcalculates three feature amounts of a first deviation between thethickness target value and a thickness measurement value of a pointclosest to the first compression mechanism among the three or morepoints, a second deviation between the thickness target value and athickness measurement value of a point closest to the second compressionmechanism among the three or more points, and a secondary component of athickness profile of the electrode plate, and adaptively changes thesetting values of the first compression mechanism, the secondcompression mechanism, the first bend mechanism, and the second bendmechanism on the basis of the three feature amounts.
 2. The roll pressdevice according to claim 1, wherein the thickness meter is provided onthe exit side of the first pressure roller and the second pressureroller, and detects the thickness of the electrode plate of thesecondary battery at each of a first point, a second point, and a thirdpoint arranged in the width direction of the electrode plate, thecalculator calculates setting values of the first compression mechanism,the second compression mechanism, the first bend mechanism, and thesecond bend mechanism on the basis of a first point thicknessmeasurement value, a second point thickness measurement value, and athird point thickness measurement value based on detection values of thethickness meter and the thickness target value, the first point is setto an end portion of the electrode plate of the secondary battery on theside where the first compression mechanism is provided, the second pointis set to a center portion of the electrode plate of the secondarybattery, the third point is set to an end portion of the electrode plateof the secondary battery on the side where the second compressionmechanism is provided, the calculator calculates three feature amountsof a first deviation between the first point thickness measurement valueand the thickness target value, a second deviation between the thirdpoint thickness measurement value and the thickness target value, and asecondary component of a thickness profile of the electrode plate fromthe first point thickness measurement value, the second point thicknessmeasurement value, the third point thickness measurement value, and thethickness target value, and the secondary component of the thicknessprofile of the electrode plate is defined by a difference between thesecond point thickness measurement value and an average value of thefirst point thickness measurement value and the third point thicknessmeasurement value.
 3. The roll press device according to claim 1,wherein the calculator calculates setting values of the firstcompression mechanism, the second compression mechanism, the first bendmechanism, and the second bend mechanism such that all of the threefeature amounts become zero, on the basis of a relation between a loadgenerated by the first compression mechanism, the second compressionmechanism, the first bend mechanism, and the second bend mechanism andthe three feature amounts, which is derived in advance.
 4. The rollpress device according to claim 3, wherein the first compressionmechanism includes a first press cylinder, the second compressionmechanism includes a second press cylinder, the first bend mechanismincludes a first bend cylinder, the second bend mechanism includes asecond bend cylinder, and the calculator calculates setting values of apressure of the first press cylinder, a pressure of the second presscylinder, a pressure of the first bend cylinder, and a pressure of thesecond bend cylinder such that all of the three feature amounts becomezero.
 5. The roll press device according to claim 3, wherein the firstcompression mechanism includes a first press cylinder, the secondcompression mechanism includes a second press cylinder, the first bendmechanism includes a first bend cylinder, the second bend mechanismincludes a second bend cylinder, and the calculator calculates settingvalues of a position of the first press cylinder, a position of thesecond press cylinder, a pressure of the first bend cylinder, and apressure of the second bend cylinder such that all of the three featureamounts become zero.
 6. The roll press device according to claim 5,wherein the first compression mechanism further includes a firstmagnescale to measure a position of the first press cylinder, the secondcompression mechanism further includes a second magnescale to measure aposition of the second press cylinder, and the controller controls thepressure of the first press cylinder such that the position of the firstpress cylinder measured by the first magnescale and the position of thefirst press cylinder supplied from the calculator are matched with eachother, and controls the pressure of the second press cylinder such thatthe position of the second press cylinder measured by the secondmagnescale and the position of the second press cylinder supplied fromthe calculator are matched with each other.
 7. The roll press deviceaccording to claim 3, wherein the first compression mechanism includes afirst electric screw, the second compression mechanism includes a secondelectric screw, the first bend mechanism includes a first bend cylinder,the second bend mechanism includes a second bend cylinder, and thecalculator calculates setting values of a position of the first electricscrew, a position of the second electric screw, a pressure of the firstbend cylinder, and a pressure of the second bend cylinder such that allof the three feature amounts become zero.
 8. The roll press deviceaccording to claim 3, wherein the first compression mechanism includes afirst electric cotter, the second compression mechanism includes asecond electric cotter, the first bend mechanism includes a first bendcylinder, the second bend mechanism includes a second bend cylinder, andthe calculator calculates setting values of a height of the firstelectric cotter, a height of the second electric cotter, a pressure ofthe first bend cylinder, and a pressure of the second bend cylinder suchthat all of the three feature amounts become zero.
 9. The roll pressdevice according to claim 1, wherein the thickness meter continuouslydetects a thickness of the electrode plate by scanning one thicknessdetection sensor in a width direction of the electrode plate, andextracts thickness detection values at the three or more points.
 10. Theroll press device according to claim 1, wherein the thickness meterdetects thicknesses at the three or more points with three or morethickness detection sensors.
 11. The roll press device according toclaim 9, further comprising: a thickness measurement value calculatorstructured to calculate thickness measurement values at the three ormore points by filtering the three or more thickness detection valuesdetected by the thickness meter in a longitudinal direction of theelectrode plate.
 12. The roll press device according to claim 1, whereinthe calculator suspends a next change of the setting values of the firstcompression mechanism, the second compression mechanism, the first bendmechanism, and the second bend mechanism until predetermined conditionsregarding a pass line length from a press position to the thicknessmeter and a reflection time of the changing of the setting values in anactual output after changing the setting values of the first compressionmechanism, the second compression mechanism, the first bend mechanism,and the second bend mechanism are satisfied.
 13. A control device usedin a roll press device, which includes a first pressure roller and asecond pressure roller rolling an electrode plate of a secondary batteryto be continuously conveyed by sandwiching the electrode plate; a firstmain bearing and a second main bearing provided on one side and theother side of a rotation shaft of the first pressure roller,respectively, and rotatably supporting the rotation shaft; a third mainbearing and a fourth main bearing provided on one side and the otherside of a rotation shaft of the second pressure roller, respectively,and rotatably supporting the rotation shaft; a first bend bearing and asecond bend bearing provided on one side and the other side of therotation shaft of the first pressure roller, respectively, and rotatablysupporting the rotation shaft; a third bend bearing and a fourth bendbearing provided on one side and the other side of the rotation shaft ofthe second pressure roller, respectively, and rotatably supporting therotation shaft; a first compression mechanism capable of applying a loadto at least one of the first main bearing and the third main bearing ina direction in which the first pressure roller and the second pressureroller approach each other; a second compression mechanism capable ofapplying a load to at least one of the second main bearing and thefourth main bearing in a direction in which the first pressure rollerand the second pressure roller approach each other; a first bendmechanism capable of applying a load to at least one of the first bendbearing and the third bend bearing in a direction in which the firstpressure roller and the second pressure roller are separated from eachother; a second bend mechanism capable of applying a load to at leastone of the second bend bearing and the fourth bend bearing in adirection in which the first pressure roller and the second pressureroller are separated from each other; and a thickness meter provided onthe exit side of the first pressure roller and the second pressureroller and detecting a thickness of the electrode plate of the secondarybattery at three or more points in a width direction of the electrodeplate, the control device comprising: a calculator structured tocalculate setting values of the first compression mechanism, the secondcompression mechanism, the first bend mechanism, and the second bendmechanism on the basis of thickness measurement values at the three ormore points based on detection values of the thickness meter and athickness target value; and a controller structured to control loads ofthe first compression mechanism, the second compression mechanism, thefirst bend mechanism, and the second bend mechanism on the basis of thesetting values calculated by the calculator, wherein the calculatorcalculates three feature amounts of a first deviation between thethickness target value and a thickness measurement value of a pointclosest to the first compression mechanism among the three or morepoints, a second deviation between the thickness target value and athickness measurement value of a point closest to the second compressionmechanism among the three or more points, and a secondary component of athickness profile of the electrode plate, and adaptively changes thesetting values of the first compression mechanism, the secondcompression mechanism, the first bend mechanism, and the second bendmechanism on the basis of the three feature amounts.